Co-rotating scroll compressor

ABSTRACT

This co-rotating scroll compressor is provided with: a first side plate (27) which is arranged on the side of a drive-side rotational axis direction (CL1) with respect to a drive-side scroll member (70) and a driven-side scroll member (90), a second side plate (30) fixed at a predetermined gap in the direction of the drive-side rotational axis (CL1) with respect to the first side plate (27), and a center plate (20) arranged between the first side plate (27) and the second side plate (30). The first side plate (27) is fixed to the driven-side scroll member (90), and the center plate (20) is fixed to the drive-side scroll member (70). A synchronization drive mechanism equipped with a crank pin (15) is disposed between the first side plate (27) and second side plate (30) and the center plate (20).

TECHNICAL FIELD

The present invention relates to a co-rotating scroll compressor.

BACKGROUND ART

A co-rotating scroll compressor is known in the related art (see PTL 1).The co-rotating scroll compressor is provided with a drive-side scrolland a driven-side scroll rotating synchronously with the drive-sidescroll. A driven shaft supporting the rotation of the driven-side scrollis offset by a turning radius with respect to a drive shaft rotating thedrive-side scroll. As a result, the drive shaft and the driven shaft arerotated in the same direction and at the same angular velocity.

CITATION LIST Patent Literature

[PTL 1] Japanese Patent No. 5443132

SUMMARY OF INVENTION Technical Problem

In the co-rotating scroll compressor, a synchronization drive mechanismtransmitting a drive force from a drive-side scroll member to adriven-side scroll member is used such that the drive-side scroll memberand the driven-side scroll member perform rotating motions in the samedirection and at the same angular velocity. Although a mechanism using acrank pin or a pin ring is conceivable as the synchronization drivemechanism, the life of the synchronization drive mechanism may beshortened due to compression heat transmission from the scroll member. Adecrease in the life of the synchronization drive mechanism needs to beprevented particularly in a case where a lubricant is used.

When the synchronization drive mechanism is adopted between the twomembers, that is, the drive-side scroll member and the driven-sidescroll member, a load is applied to the synchronization drive mechanismat two places, which may result in moment generation around thesynchronization drive mechanism and a decrease in the life of thesynchronization drive mechanism.

In a case where a pin ring or a crank pin provided with a rollingbearing is used as the synchronization drive mechanism, the lubricantthat is enclosed in the rolling bearing may leak to the outside due to acentrifugal force, and then a decrease in bearing life may result frominsufficient lubrication. In addition, the lubricant leakage may resultin mixing into a compressed fluid and fluid contamination.

In a case where the crank pin provided with the rolling bearing is usedas the synchronization drive mechanism, it is necessary to provide atleast two rolling bearings supporting crank pin rotation, which leads toan increase in cost.

In a case where the crank pin provided with the rolling bearing is usedas the synchronization drive mechanism, the tolerance of the crank pin,the tolerance of the hole into which the rolling bearing is inserted, orthe like may lead to internal force generation in the crank pin and adecrease in the life of the synchronization drive mechanism. In a casewhere cutting is performed with the crank pin integrated in particular,a crank pin machining error is likely to occur and the internal forcethat is generated in the crank pin may increase.

The present invention has been made in view of such circumstances, andan object of the present invention is to provide a co-rotating scrollcompressor with which the life of a synchronization drive mechanism canbe extended.

An object of the present invention is to provide a co-rotating scrollcompressor with which the cost of a synchronization drive mechanism canbe reduced.

An object of the present invention is to provide a co-rotating scrollcompressor with which the life of a synchronization drive mechanism thatis a crank pin mechanism can be extended.

Solution to Problem

A co-rotating scroll compressor according to an aspect of the presentinvention includes a drive-side scroll member driven to rotate around arotational axis by a drive unit and having a spiral drive-side wall bodydisposed on a drive-side end plate, a driven-side scroll member in whicha spiral driven-side wall body corresponding to the drive-side wall bodyis disposed on a driven-side end plate and the driven-side wall bodymeshes with the drive-side wall body to form a compression space, asynchronization drive mechanism transmitting a drive force of the driveunit to the driven-side scroll member such that the drive-side scrollmember and the driven-side scroll member perform rotating motions in thesame direction and at the same angular velocity, a first side platedisposed on the rotational axis direction side with respect to thedrive-side scroll member and the driven-side scroll member, a secondside plate fixed at a predetermined gap in the rotational axis directionwith respect to the first side plate, and a center plate disposedbetween the first side plate and the second side plate. The first sideplate is fixed to one of the drive-side scroll member and thedriven-side scroll member. The center plate is fixed to the other of thedrive-side scroll member and the driven-side scroll member. Thesynchronization drive mechanism is provided between the first and secondside plates and the center plate.

The compression space is formed by the drive-side wall body disposed onthe drive-side end plate of the drive-side scroll member and thedriven-side wall body of the driven-side scroll member meshing with eachother. The drive-side scroll member is driven to rotate by the driveunit and the drive force is transmitted to the driven-side scroll membervia the synchronization drive mechanism. As a result, the driven-sidescroll member rotates and performs a rotating motion in the samedirection and at the same angular velocity with respect to thedrive-side scroll member. Provided in this manner is the co-rotatingscroll compressor in which both the drive-side scroll member and thedriven-side scroll member rotate.

The first side plate and the second side plate are provided on therotational axis direction side with respect to the drive-side scrollmember and the driven-side scroll member and the center plate isprovided between the side plates. The synchronization drive mechanism isprovided between both side plates and the center plate. Since the sideplates and the center plate as members separate from both scroll membersare provided with the synchronization drive mechanisms as describedabove, heating attributable to the compression heat from the scrollmembers can be decreased and the life of the synchronization drivemechanisms can be extended.

A load is applied to the synchronization drive mechanism from the centerplate and the side plates on both sides thereof, and thus the momentaround the center plate can be canceled and the life of thesynchronization drive mechanisms can be extended.

The synchronization drive mechanisms are disposed by both side platesand the center plate being provided on the rotational axis directionside, and thus diameter reduction can be achieved as compared with acase where a synchronization drive mechanism is provided on radialdirection sides of the scroll members.

In the co-rotating scroll compressor according to an aspect of thepresent invention, the synchronization drive mechanism is provided witha crank pin having an eccentric shaft portion having an eccentric axiswhich is eccentric to a central axis of a central cylindrical portionand a crank pin end portion rolling bearing provided between both endportions of the eccentric shaft portion and the first and second sideplates and an urging member urging an inner ring of the crank pin endportion rolling bearing toward a leading edge of the eccentric shaftportion in the eccentric axis direction is provided between the innerring and the eccentric shaft portion.

The crank pin and the crank pin end portion rolling bearing constitutethe synchronization drive mechanism and the crank pin end portionrolling bearing rotatably and pivotally supports both end portions ofthe crank pin with both side plates. The urging member urging the innerring toward the leading edge of the eccentric shaft portion in theeccentric axis direction is provided between the inner ring of the crankpin end portion rolling bearing and the eccentric shaft portion of thecrank pin. The urging member urges the inner ring of the crank pin endportion rolling bearing toward the leading edge, and thus an outer ringis pressed against the side plate via the rolling body of the crank pinend portion rolling bearing. As a result, the crank pin end portionrolling bearing is put into a state where a preload is applied betweenthe eccentric bearing of the crank pin and the side plate, it ispossible to prevent slipping between the rolling body and the inner ringand slipping between the inner ring and the eccentric shaft portion, andthe life of the synchronization drive mechanism can be extended.

An O-ring or the like is used as the urging member.

In the co-rotating scroll compressor according to an aspect of thepresent invention, the synchronization drive mechanism is provided witha crank pin having an eccentric shaft portion having an eccentric axiswhich is eccentric to a central axis of a central cylindrical portionand a crank pin end portion rolling bearing provided between both endportions of the eccentric shaft portion and the first and second sideplates and a preload is applied to the crank pin end portion rollingbearing in the eccentric axis direction by a gap between the first sideplate and the second side plate.

The crank pin and the crank pin end portion rolling bearing constitutethe synchronization drive mechanism and the crank pin end portionrolling bearing rotatably and pivotally supports both end portions ofthe crank pin with both side plates. A preload is applied to the crankpin end portion rolling bearing in the eccentric axis direction by thegap between the first side plate and the second side plate. As a result,it is possible to prevent slipping between the rolling body of the crankpin end portion rolling bearing and the inner ring and slipping betweenthe inner ring and the eccentric shaft portion and the life of thesynchronization drive mechanism can be extended.

By a specific preload application method, the gap between the sideplates is narrowed when the second side plate is fastened to the firstside plate. In other words, the gap determined by both side plates beingfastened is kept smaller than the gap between both side platesdetermined by the crank pin end portion rolling bearing and the crankpin of the synchronization drive mechanism.

In the co-rotating scroll compressor according to an aspect of thepresent invention, the synchronization drive mechanism is provided witha crank pin having an eccentric shaft portion having an eccentric axiswhich is eccentric to a central axis of a central cylindrical portionand a crank pin end portion rolling bearing provided between both endportions of the eccentric shaft portion and the first and second sideplates and an elastic body is provided between an inner peripheralsurface of an inner ring of the crank pin end portion rolling bearingand an outer peripheral surface of the eccentric shaft portion.

The crank pin and the crank pin end portion rolling bearing constitutethe synchronization drive mechanism and the crank pin end portionrolling bearing rotatably and pivotally supports both end portions ofthe crank pin with both side plates. The elastic body is providedbetween the inner peripheral surface of the inner ring of the crank pinend portion rolling bearing and the outer peripheral surface of theeccentric shaft portion. As a result, a reaction force is generated bythe elastic body sandwiched between the inner ring and the eccentricshaft portion being deformed, slipping between the eccentric shaftportion and the inner ring can be prevented, and the life of thesynchronization drive mechanism can be extended.

In the co-rotating scroll compressor according to an aspect of thepresent invention, among a fixing portion of the first side plate whichis fixed to one of the drive-side scroll member and the driven-sidescroll member and a fixing portion of the center plate which is fixed tothe other of the drive-side scroll member and the driven-side scrollmember, the fixing portion positioned on a radial inner side of a centerof the scroll member has a structure in which a resin portion isinterposed, and the fixing portion positioned on a radial outer side ofthe center of the scroll member has a structure using a metal portionwithout resin portion interposition.

The structure in which the resin portion is interposed is because thetemperature of the fixing portion positioned on the radial inner side ofthe center of the scroll member tends to rise due to compression heat.As a result, it is possible to achieve life extension by suppressing arise in the temperature of the synchronization drive mechanism.

The metallic structure without resin portion interposition is because arise in temperature attributable to compression heat has little effecton the fixing portion positioned radially outward of the center of thescroll member. As a result, the fixing portion can be accuratelyassembled by means of metal, and thus the synchronization drivemechanism can be accurately positioned, phase shift reduction can beachieved between the drive-side scroll member and the driven-side scrollmember, and compression performance improvement can be achieved.

The co-rotating scroll compressor according to an aspect of the presentinvention includes a drive-side scroll member driven to rotate around arotational axis by a drive unit and having a spiral drive-side wall bodydisposed on a drive-side end plate, a driven-side scroll member in whicha spiral driven-side wall body corresponding to the drive-side wall bodyis disposed on a driven-side end plate and the driven-side wall bodymeshes with the drive-side wall body to form a compression space, asynchronization drive mechanism transmitting a drive force to thedriven-side scroll member such that the drive-side scroll member and thedriven-side scroll member perform rotating motions in the same directionand at the same angular velocity, a first side plate disposed on therotational axis direction side with respect to the drive-side scrollmember and the driven-side scroll member, a second side plate fixed at apredetermined gap in the rotational axis direction with respect to thefirst side plate, and a center plate disposed between the first sideplate and the second side plate. The first side plate is fixed to one ofthe drive-side scroll member and the driven-side scroll member. Thecenter plate is fixed to the other of the drive-side scroll member andthe driven-side scroll member. The synchronization drive mechanism isprovided between the first and second side plates and the center plate.A peripheral wall portion surrounding an outer peripheral side of thecenter plate is provided between the first side plate and the secondside plate.

The compression space is formed by the drive-side wall body disposed onthe drive-side end plate of the drive-side scroll member and thedriven-side wall body of the driven-side scroll member meshing with eachother. The drive-side scroll member is driven to rotate by the driveunit and the drive force is transmitted to the driven-side scroll membervia the synchronization drive mechanism. As a result, the driven-sidescroll member rotates and performs a rotating motion in the samedirection and at the same angular velocity with respect to thedrive-side scroll member. Provided in this manner is the co-rotatingscroll compressor in which both the drive-side scroll member and thedriven-side scroll member rotate.

The first side plate and the second side plate are provided on therotational axis direction side with respect to the drive-side scrollmember and the driven-side scroll member and the center plate isprovided between the side plates. The synchronization drive mechanism isprovided between both side plates and the center plate. The peripheralwall portion surrounding the outer peripheral side of the center plateis provided between the first side plate and the second side plate. As aresult, even when the lubricant supplied to the synchronization drivemechanism is moved to the outer peripheral side by a centrifugal force,the lubricant can be held on the inner peripheral side of the peripheralwall portion, and thus an insufficient lubrication of thesynchronization drive mechanism can be avoided and life extension can beachieved.

Usable as the synchronization drive mechanism is, for example, a crankmechanism provided with a crank pin having an eccentric shaft portionhaving an eccentric axis which is eccentric to a central axis of acentral cylindrical portion and a crank pin end portion rolling bearingprovided between both end portions of the eccentric shaft portion andthe first and second side plates. The rolling bearing is supplied with alubricant.

The co-rotating scroll compressor according to an aspect of the presentinvention further includes a drive shaft portion rotating around therotational axis and connected between the drive-side end plate and thedrive unit. The center plate is fixed to the drive shaft portion. A holeportion for the first side plate through which the drive shaft portionpasses is formed in the first side plate. A hole portion for the secondside plate through which the drive shaft portion passes is formed in thesecond side plate. A first seal member is provided between the holeportion for the first side plate and the drive shaft portion and/orbetween the hole portion for the second side plate and the drive shaftportion.

The drive shaft portion is provided between the drive-side end plate andthe drive unit and the center plate is fixed to the drive shaft portion.As a result, a drive force is transmitted from the drive unit to thedrive-side scroll member via the center plate.

The hole portions through which the drive shaft portion passes arerespectively provided in the first side plate and the second side plate.As a result, a gap is inevitably formed between both side plates and thedrive shaft portion. The first seal member is provided so as to seal thegap. As a result, it is possible to prevent lubricant leakage from thespace between both side plates and the drive shaft portion.

A boots seal, a labyrinth seal, or the like can be adopted as the firstseal member.

The co-rotating scroll compressor according to an aspect of the presentinvention further includes a drive shaft portion rotating around therotational axis and connected between the drive-side end plate and thedrive unit. The center plate is fixed to the drive shaft portion. A holeportion for the first side plate through which the drive shaft portionpasses is formed in the first side plate. A hole portion for the secondside plate through which the drive shaft portion passes is formed in thesecond side plate. A second seal member is provided between the firstside plate and the center plate and/or between the second side plate andthe center plate.

The drive shaft portion is provided between the drive-side end plate andthe drive unit and the center plate is fixed to the drive shaft portion.As a result, a drive force is transmitted from the drive unit to thedrive-side scroll member via the center plate.

The hole portions through which the drive shaft portion passes arerespectively provided in the first side plate and the second side plate.As a result, a gap is inevitably formed between both side plates and thedrive shaft portion. The second seal member is provided between bothside plates and the center plate. As a result, it is possible to preventlubricant leakage from the space between both side plates and the driveshaft portion.

Adoptable as the second seal member is, for example, a tip seal insertedin a circumferential groove formed in each side plate or the centerplate.

In the co-rotating scroll compressor according to an aspect of thepresent invention, the first side plate is fixed to the drive-side wallbody on an outer peripheral side, the second side plate is fixed to thefirst side plate, the drive unit is connected to a rotation center ofthe second side plate, the center plate is fixed to a driven shaftportion connected to a rotation center of the driven-side end plate, ahole portion for the first side plate through which the driven shaftportion passes is formed in the first side plate, and a rotation centerregion of the second side plate is closed by a wall portion.

The first side plate is fixed to the drive-side wall body on the outerperipheral side, the second side plate is fixed to the first side plate,and the drive unit is connected to a substantial rotation center of thesecond side plate. As a result, a drive force is transmitted from thedrive unit to the drive-side scroll member via the first side plate andthe second side plate.

The drive force transmitted from both side plates via thesynchronization drive mechanism is guided from the center plate to thedriven-side scroll member by the center plate being fixed to the drivenshaft portion connected to the rotation center of the driven-side endplate.

The driven shaft portion is disposed so as to pass through the holeportion for the first side plate formed in the first side plate. Since adrive force is transmitted from the center plate to the driven shaftportion via the synchronization drive mechanism, there is no need toform a hole portion for penetration by the driven shaft portion in therotation center region of the second side plate. Accordingly, it ispossible to adopt the second side plate that has a rotation centerregion closed by a wall portion, and thus lubricant leakage from therotation center of the second side plate can be prevented.

The co-rotating scroll compressor according to an aspect of the presentinvention includes a drive-side scroll member driven to rotate around arotational axis by a drive unit and having a spiral drive-side wall bodydisposed on a drive-side end plate, a driven-side scroll member in whicha spiral driven-side wall body corresponding to the drive-side wall bodyis disposed on a driven-side end plate and the driven-side wall bodymeshes with the drive-side wall body to form a compression space, asynchronization drive mechanism transmitting a drive force of the driveunit to the driven-side scroll member such that the drive-side scrollmember and the driven-side scroll member perform rotating motions in thesame direction and at the same angular velocity, a first side platedisposed on the rotational axis direction side with respect to thedrive-side scroll member and the driven-side scroll member, a secondside plate fixed at a predetermined gap in the rotational axis directionwith respect to the first side plate, and a center plate disposedbetween the first side plate and the second side plate. The first sideplate is fixed to one of the drive-side scroll member and thedriven-side scroll member. The center plate is fixed to the other of thedrive-side scroll member and the driven-side scroll member. Thesynchronization drive mechanism is provided with a round bar-shaped pinprovided between the first and second side plates and the center plateand a ring guiding the pin by an inner peripheral surface of the ringabutting against an outer periphery of the pin.

A pin ring mechanism provided with the round bar-shaped pin and the ringis adopted as the synchronization drive mechanism. As a result, it ispossible to realize the synchronization drive mechanism without adoptinga crank pin mechanism, and thus it is possible to achieve cost reductionwithout a complex configuration caused by a large number of bearingsbeing adopted as in the case of crank pin mechanisms.

In the co-rotating scroll compressor according to an aspect of thepresent invention, the ring is a rolling bearing provided on the centerplate and both ends of the pin are press-fitted to the first side plateand the second side plate and a longitudinal central portion of the pinabuts against an inner peripheral surface of the rolling bearing.

The pin is press-fitted and fixed to both side plates, and thus the pincan be used as a positioning pin for both side plates.

Both ends of the pin are fixed to both side plates and the centralportion of the pin abuts against the inner peripheral surface of therolling bearing. Accordingly, inclination of the inner ring of therolling bearing can be prevented, an oblique movement of a rollingmember such as a ball can be prevented, and the life of thesynchronization drive mechanism can be extended.

In the co-rotating scroll compressor according to an aspect of thepresent invention, the ring is a rolling bearing provided on the centerplate and one end of the pin is press-fitted to one of the first sideplate and the second side plate, the other end of the pin is fixed tothe other of the first side plate and the second side plate via anelastic body, and a longitudinal central portion of the pin abutsagainst an inner peripheral surface of the rolling bearing.

One end of the pin is press-fitted and fixed to one of the side platesand the other end of the pin is fixed to the other of the side platesvia the elastic body. As a result, both ends of the pin being incapableof being press-fitted to both side plates due to a component tolerancecan be prevented, assembly can be facilitated, and cost reduction can beachieved.

In the co-rotating scroll compressor according to an aspect of thepresent invention, three or more synchronization drive mechanisms areprovided to be spaced apart in a circumferential direction of therotational axis, in two of the synchronization drive mechanisms, thering is a rolling bearing provided on the center plate, both ends of thepin are press-fitted to the first side plate and the second side plate,and a longitudinal central portion of the pin abuts against an innerperipheral surface of the rolling bearing, and in the othersynchronization drive mechanism, the ring is a rolling bearing providedon the center plate, one end of the pin is press-fitted to one of thefirst side plate and the second side plate, the other end of the pin isfixed to the other of the first side plate and the second side plate viaan elastic body, and a longitudinal central portion of the pin abutsagainst an inner peripheral surface of the rolling bearing.

Two out of the three or more synchronization drive mechanisms have afunction as a positioning pin as a configuration in which both ends ofthe pin are press-fitted and fixed to both side plates. As for the pinof the other synchronization drive mechanism, one end is press-fittedand fixed and the other end is fixed via the elastic body, which resultsin tolerance absorption. As a result, both side plates can be positionedby means of the synchronization drive mechanism and assemblabilityimprovement can be achieved.

In the co-rotating scroll compressor according to an aspect of thepresent invention, the ring is a rolling bearing provided on each of thefirst side plate and the second side plate and a longitudinal centralportion of the pin is press-fitted to the center plate and both ends ofthe pin abut against an inner peripheral surface of the rolling bearing.

The central portion of the pin is press-fitted to the center plate andboth ends of the pin abut against the inner peripheral surfaces of therolling bearings provided on both side plates. Accordingly, both ends ofthe pin are not restrained by both side plates, and thus it is possibleto avoid a situation in which the pin cannot be fixed during assemblydue to the component tolerance of both side plates. As a result,assemblability improvement can be achieved.

In the co-rotating scroll compressor according to an aspect of thepresent invention, the ring is a slide bearing instead of the rollingbearing.

It is possible to achieve cost reduction by replacing the rollingbearing with the slide bearing (such as a floating bush bearing).

The moment of inertia of a rotation system such as the rolling bearingcan be reduced, and thus response enhancement can be achieved.

The co-rotating scroll compressor according to an aspect of the presentinvention includes a drive-side scroll member driven to rotate around arotational axis by a drive unit and having a spiral drive-side wall bodydisposed on a drive-side end plate, a driven-side scroll member in whicha spiral driven-side wall body corresponding to the drive-side wall bodyis disposed on a driven-side end plate and the driven-side wall bodymeshes with the drive-side wall body to form a compression space, asynchronization drive mechanism transmitting a drive force of the driveunit to the driven-side scroll member such that the drive-side scrollmember and the driven-side scroll member perform rotating motions in thesame direction and at the same angular velocity, a first side platedisposed on the rotational axis direction side with respect to thedrive-side scroll member and the driven-side scroll member, a secondside plate fixed at a predetermined gap in the rotational axis directionwith respect to the first side plate, and a center plate disposedbetween the first side plate and the second side plate. The first sideplate is fixed to one of the drive-side scroll member and thedriven-side scroll member. The center plate is fixed to the other of thedrive-side scroll member and the driven-side scroll member. Thesynchronization drive mechanism is provided between the first and secondside plates and the center plate and is provided with a crank pin havingan eccentric shaft portion having an eccentric axis which is eccentricto a central axis of a central cylindrical portion, a first crank pinend portion rolling bearing provided between one end of the eccentricshaft portion and the first side plate, a second crank pin end portionrolling bearing provided between the other end of the eccentric shaftportion and the second side plate, and a cylindrical portion rollingbearing provided between the cylindrical portion and the center plate.An elastic body is provided in at least one of spaces between an outerring of the first crank pin end portion rolling bearing and the firstside plate, between an outer ring of the second crank pin end portionrolling bearing and the second side plate, and between an outer ring ofthe cylindrical portion rolling bearing and the center plate or in atleast one of spaces between an inner ring of the first crank pin endportion rolling bearing and the one end of the eccentric shaft portion,between an inner ring of the second crank pin end portion rollingbearing and the other end of the eccentric shaft portion, and between aninner ring of the cylindrical portion rolling bearing and thecylindrical portion.

The elastic body is provided between the outer ring of the rollingbearing of the synchronization drive mechanism and the side plate or thecenter plate or between the inner ring of the rolling bearing of thesynchronization drive mechanism and the crank pin. As a result, thetolerance of the crank pin, the side plates, and the center plate can beabsorbed by the elastic body being deformed, internal force generationin the crank pin can be avoided, and the life of the synchronizationdrive mechanism can be extended.

In addition, the machining tolerance of the crank pin can be mitigatedand machining and management costs can be reduced.

In addition, the outer ring is pressed to the inner ring side by theelastic body, and thus it is possible to prevent slipping between theouter ring and the hole in which the outer ring is fitted.

In the co-rotating scroll compressor according to an aspect of thepresent invention, the elastic body is provided between the outer ringof the cylindrical portion rolling bearing and the center plate, theouter ring of the first crank pin end portion rolling bearing ispress-fitted to the first side plate, and the outer ring of the secondcrank pin end portion rolling bearing is press-fitted to the second sideplate.

The outer ring of the first crank pin end portion rolling bearing andthe outer ring of the second crank pin end portion rolling bearing arepress-fitted, and thus a centrifugal force is held by both crank pin endportion rolling bearings. The two rolling bearings bear the centrifugalforce in this manner, and thus the load to be borne can be mitigated ascompared with a case where the single cylindrical portion rollingbearing bears the centrifugal force.

In addition, the crank pin is supported at both ends by the two crankpin end portion rolling bearings, and thus the posture of the crank pincan be stabilized.

In the co-rotating scroll compressor according to an aspect of thepresent invention, an insertion hole into which the eccentric shaftportion is inserted is formed in the cylindrical portion.

The eccentric shaft portion of the crank pin is inserted into theinsertion hole formed in the cylindrical portion. As a result, theeccentric shaft portion and the cylindrical portion can be separatecomponents and can be machined separately as for the crank pin.Accordingly, the axial centers at both ends of the eccentric shaftportion can be aligned as compared with a case where the eccentric shaftportion and the cylindrical portion are integrally machined.

The co-rotating scroll compressor according to an aspect of the presentinvention includes a drive-side scroll member driven to rotate around arotational axis by a drive unit and having a spiral drive-side wall bodydisposed on a drive-side end plate, a driven-side scroll member in whicha spiral driven-side wall body corresponding to the drive-side wall bodyis disposed on a driven-side end plate the driven-side wall body mesheswith the drive-side wall body to form a compression space, asynchronization drive mechanism transmitting a drive force of the driveunit to the driven-side scroll member such that the drive-side scrollmember and the driven-side scroll member perform rotating motions in thesame direction and at the same angular velocity, a first side platedisposed on the rotational axis direction side with respect to thedrive-side scroll member and the driven-side scroll member, a secondside plate fixed at a predetermined gap in the rotational axis directionwith respect to the first side plate, and a center plate disposedbetween the first side plate and the second side plate. The first sideplate is fixed to one of the drive-side scroll member and thedriven-side scroll member. The center plate is fixed to the other of thedrive-side scroll member and the driven-side scroll member. Thesynchronization drive mechanism is provided between the first and secondside plates and the center plate and is provided with a crank pin havingan eccentric shaft portion having an eccentric axis which is eccentricto a central axis of a central cylindrical portion. An insertion holeinto which the eccentric shaft portion is inserted is formed in thecylindrical portion.

The eccentric shaft portion of the crank pin is inserted into theinsertion hole formed in the cylindrical portion. As a result, theeccentric shaft portion and the cylindrical portion can be separatecomponents and can be machined separately. Accordingly, the axialcenters at both ends of the eccentric shaft portion can be aligned ascompared with a case where the eccentric shaft portion and thecylindrical portion are integrally machined.

Accordingly, an internal force applied to the crank pin can be reducedand the life of the synchronization drive mechanism can be extended.

Advantageous Effects of Invention

Since the side plates and the center plate as members separate from thedrive-side scroll member and the driven-side scroll member are providedwith the synchronization drive mechanisms, heating attributable to thecompression heat from the scroll members can be decreased and the lifeof the synchronization drive mechanisms can be extended.

The peripheral wall portion surrounding the outer peripheral side of thecenter plate is provided between the first side plate and the secondside plate and the lubricant is held on the inner peripheral side of theperipheral wall portion, and thus the life of the synchronization drivemechanisms can be extended.

It is possible to simplify the configuration of the synchronizationdrive mechanism and achieve cost reduction by adopting the pin ringmechanism.

Tolerance absorption is performed by the elastic body being deformed,and thus internal force generation in the crank pin can be avoided andthe life of the synchronization drive mechanisms can be extended.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a longitudinal cross-sectional view illustrating a co-rotatingscroll compressor according to a first embodiment of the presentinvention.

FIG. 2 is a perspective view illustrating a scroll member, both sideplates, and a center plate of the co-rotating scroll compressorillustrated in FIG. 1.

FIG. 3 is a plan view illustrating the first drive-side scroll partillustrated in FIG. 1.

FIG. 4 is a plan view illustrating the second drive-side scroll partillustrated in FIG. 1.

FIG. 5 is a longitudinal cross-sectional view illustrating a secondembodiment of the present invention and a part around a synchronizationdrive mechanism.

FIG. 6 is a longitudinal cross-sectional view illustrating ModificationExample 1 of the second embodiment.

FIG. 7 is a longitudinal cross-sectional view illustrating ModificationExample 2 of the second embodiment.

FIG. 8 is a longitudinal cross-sectional view illustrating a thirdembodiment of the present invention and a part around thesynchronization drive mechanism.

FIG. 9 is a longitudinal cross-sectional view illustrating theco-rotating scroll compressor according to a fourth embodiment of thepresent invention.

FIG. 10 is a plan view illustrating the first drive-side wall bodyillustrated in FIG. 9.

FIG. 11 is a plan view illustrating the first driven-side wall bodyillustrated in FIG. 9.

FIG. 12 is a plan view illustrating the side plate and the center plate.

FIG. 13 is a longitudinal cross-sectional view illustrating aco-rotating scroll compressor according to a fifth embodiment of thepresent invention.

FIG. 14 is a longitudinal cross-sectional view illustrating aco-rotating scroll compressor according to a sixth embodiment of thepresent invention.

FIG. 15 is a longitudinal cross-sectional view illustrating aco-rotating scroll compressor according to a seventh embodiment of thepresent invention.

FIG. 16 is a plan view illustrating the first drive-side wall bodyillustrated in FIG. 15.

FIG. 17 is a plan view illustrating the first driven-side wall bodyillustrated in FIG. 15.

FIG. 18 is a plan view illustrating the side plate and the center plate.

FIG. 19 is an enlarged longitudinal cross-sectional view illustrating apart around a pin ring mechanism.

FIG. 20 is a longitudinal cross-sectional view illustrating amodification example of the pin ring mechanism.

FIG. 21 is a longitudinal cross-sectional view illustrating a partaround the pin ring mechanism of the co-rotating scroll compressoraccording to an eighth embodiment.

FIG. 22 is a longitudinal cross-sectional view illustrating amodification example of FIG. 21.

FIG. 23 is a longitudinal cross-sectional view illustrating a pin ringmechanism provided with a slide bearing as a modification example.

FIG. 24 is a longitudinal cross-sectional view illustrating theco-rotating scroll compressor according to a ninth embodiment of thepresent invention.

FIG. 25 is a plan view illustrating the first drive-side wall bodyillustrated in FIG. 24.

FIG. 26 is a plan view illustrating the first driven-side wall bodyillustrated in FIG. 24.

FIG. 27 is a plan view illustrating the side plate and the center plate.

FIG. 28 is a longitudinal cross-sectional view illustrating a partaround an eccentric shaft portion of a crank pin.

FIG. 29 is a longitudinal cross-sectional view illustrating ModificationExample 1 of the ninth embodiment.

FIG. 30 is a longitudinal cross-sectional view illustrating ModificationExample 2 of the ninth embodiment.

FIG. 31 is a longitudinal cross-sectional view illustrating ModificationExample 3 of the ninth embodiment.

FIG. 32A is a front view illustrating the crank pin of the co-rotatingscroll compressor according to a tenth embodiment of the presentinvention.

FIG. 32B is a front view illustrating a crank pin as a reference exampleof FIG. 32A.

DESCRIPTION OF EMBODIMENTS

Hereinafter, embodiments according to the present invention will bedescribed with reference to the drawings.

First Embodiment

Hereinafter, a first embodiment of the present invention will bedescribed with reference to the drawings including FIG. 1.

FIG. 1 illustrates a co-rotating scroll compressor 1. The co-rotatingscroll compressor 1 can be used as a turbocharger compressing combustionair (a fluid) supplied to an internal combustion engine such as avehicular engine, a compressor for supplying compressed air to an airelectrode of a fuel cell, or a compressor for supplying compressed airused for a braking device of a vehicle such as a railway vehicle.

The co-rotating scroll compressor 1 is provided with a housing 3, amotor (drive unit) 5 accommodated on one end side of the housing 3, anda drive-side scroll member 70 and a driven-side scroll member 90accommodated on the other end side of the housing 3.

The housing 3 has a substantially cylindrical shape and is provided witha motor accommodation portion 3 a accommodating the motor 5 and a scrollaccommodation portion 3 b accommodating the scroll members 70 and 90.

A discharge port 3 d for discharging compressed air is formed in an endportion of the scroll accommodation portion 3 b. The housing 3 isprovided with an air intake port (not illustrated in FIG. 1) suctioningair.

The motor 5 is driven by power being supplied from a power supply source(not illustrated). The rotation of the motor 5 is controlled by acommand from a control unit (not illustrated). A stator 5 a of the motor5 is fixed to the inner peripheral side of the housing 3. A rotor 5 b ofthe motor 5 rotates around a drive-side rotational axis CL1. A driveshaft 6 extending on the drive-side rotational axis CL1 is connected tothe rotor 5 b. The drive shaft 6 is connected to a shank 20 a of acenter plate 20 driving a first drive-side scroll part 71 of thedrive-side scroll member 70.

A drive-side bearing 11 rotatably supporting the drive shaft 6 isprovided at the front end (left end in FIG. 1) of the drive shaft 6. Arear end bearing 17 rotatably supporting the drive shaft 6 between thehousing 3 and the rear end bearing 17 is provided at the rear end (rightend in FIG. 1) of the drive shaft 6, that is, in the end portion of thedrive shaft 6 that is on the side opposite to the drive-side scrollmember 70.

The drive-side scroll member 70 is provided with the first drive-sidescroll part 71 on the motor 5 side and a second drive-side scroll part72 on the discharge port 3 d side.

The first drive-side scroll part 71 is provided with a first drive-sideend plate 71 a and a first drive-side wall body 71 b.

The first drive-side end plate 71 a extends in a direction orthogonal tothe drive-side rotational axis CL1. The first drive-side end plate 71 ais fixed by means of a bolt 21 to a plurality of fixing portions 20 bprovided on the outer periphery of the center plate 20. As illustratedin FIG. 2, three fixing portions 20 b of the center plate 20 areprovided at substantially equal gaps in a circumferential direction. Thefixing portion 20 b is not limited thereto in number.

The first drive-side end plate 71 a is substantially disk-shaped in planview. As illustrated in FIG. 3, three spiral first drive-side wallbodies 71 b, that is, spiral first drive-side wall bodies 71 b in theform of three flights are provided on the first drive-side end plate 71a. The first drive-side wall bodies 71 b in the form of three flightsare disposed at equal gaps around the drive-side rotational axis CL1.Each of winding end portions 71 e of the first drive-side wall bodies 71b is independent without being fixed to the other wall portion. In otherwords, a wall portion interconnecting and reinforcing the respectivewinding end portions 71 e is not provided. The first drive-side wallbody 71 b may be one, two, or four or more in the number of flights.

As illustrated in FIG. 1, the second drive-side scroll part 72 isprovided with a second drive-side end plate 72 a and a second drive-sidewall body 72 b. The second drive-side wall body 72 b is in the form ofthree flights similarly to the first drive-side wall body 71 b (see FIG.2) described above. Each of the winding end portions of the seconddrive-side wall bodies 72 b is independent without being fixed to theother wall portion. In other words, a wall portion interconnecting andreinforcing the respective winding end portions is not provided. Thesecond drive-side wall body 72 b may be one, two, or four or more in thenumber of flights.

A second drive-side shaft portion 72 c extending in the drive-siderotational axis CL1 direction is connected to the second drive-side endplate 72 a. The second drive-side shaft portion 72 c is providedrotatably with respect to the housing 3 via a second drive-side bearing14, which is a ball bearing. The second drive-side end plate 72 a isprovided with a discharge port 72 d, which is along the drive-siderotational axis CL1.

Two seal members 26 are provided between the second drive-side shaftportion 72 c and the housing 3 and on the leading edge side (left sidein FIG. 1) of the second drive-side shaft portion 72 c beyond the seconddrive-side bearing 14. The two seal members 26 and the second drive-sidebearing 14 are disposed at predetermined gaps in the drive-siderotational axis CL1 direction. Enclosed between the two seal members 26is a lubricant that is grease such as a semi-solid lubricant. The sealmember 26 may be one in number. In this case, the lubricant is enclosedbetween the seal member 26 and the second drive-side bearing 14.

The first drive-side scroll part 71 and the second drive-side scrollpart 72 are fixed in a state where the leading edges (free ends) of thewall bodies 71 b and 72 b face each other. The first drive-side scrollpart 71 and the second drive-side scroll part 72 are fixed by a bolt 31,which is fastened to flange portions 73 provided at a plurality ofplaces in the circumferential direction so as to protrude to a radialouter side.

In the driven-side scroll member 90, a driven-side end plate 90 a ispositioned substantially at the center in an axial direction (thehorizontal direction in the drawing). A through-hole 90 h is formed atthe center of the driven-side end plate 90 a and compressed air flows tothe discharge port 72 d.

A first driven-side wall body 91 b and a second driven-side wall body 92b are provided on both sides of the driven-side end plate 90 a,respectively. The first driven-side wall body 91 b installed on themotor 5 side from the driven-side end plate 90 a meshes with the firstdrive-side wall body 71 b of the first drive-side scroll part 71 and thesecond driven-side wall body 92 b installed on the discharge port 3 dside from the driven-side end plate 90 a meshes with the seconddrive-side wall body 72 b of the second drive-side scroll part 72.

Three first driven-side wall bodies 91 b, that is, first driven-sidewall bodies 91 b in the form of three flights are provided asillustrated in FIG. 4. The driven-side wall bodies 91 b in the form ofthree flights are disposed at equal gaps around a driven-side rotationalaxis CL2. The second driven-side wall body 92 b is similar inconfiguration. Each of the driven-side wall bodies 91 b and 92 b may beone, two, or four or more in the number of flights.

A support member 33 is provided on the discharge port 3 d side (leftside in FIG. 1) of the driven-side scroll member 90. The support member33 is fixed by a bolt 25 to the leading edge (free end) of the seconddriven-side wall body 92 b.

A shank 35 a for the support member is provided on the central axis sideof the support member 33 and the shank 35 a for the support member isfixed to the housing 3 via a bearing 38 for a second support member,which is an angular ball bearing. As a result, the driven-side scrollmember rotates around the second central axis CL2 via the support member33.

A first side plate 27 is provided on the motor 5 side (right side inFIG. 1) of the driven-side scroll member 90. The first side plate 27 isfixed by a bolt 28 to the leading edge (free end) of the firstdriven-side wall body 91 b.

A second side plate 30 is provided at a predetermined gap on the motor 5side of the first side plate 27. The second side plate 30 is fixed bythe bolt 31 to the first side plate 27. A shank 30 a for the second sideplate is provided on the central axis side of the second side plate 30and the shank 30 a for the second side plate is fixed to the housing 3via a bearing 32 for the second side plate, which is an angular ballbearing. As a result, the driven-side scroll member 90 rotates aroundthe second central axis CL2 via the second side plate 30 and the firstside plate 27.

The center plate 20 is disposed between the first side plate 27 and thesecond side plate 30. As illustrated in FIG. 2, the center plate 20 isdirectly fixed to the drive-side scroll member 70 and the first sideplate 27 is directly fixed to the driven-side scroll member 90.

A crank pin 15 is provided between the first and second side plates 27and 30 and the center plate 20. The crank pin 15 has a cylindricalportion 15 a at the center and an eccentric shaft portion 15 b, whichhas an eccentric axis (see reference sign CL3 in FIG. 5) eccentric tothe central axis of the cylindrical portion 15 a.

Provided on the outer periphery of the cylindrical portion 15 a is abearing 16 for the cylindrical portion, which is an angular ballbearing. As a result, the cylindrical portion 15 a is rotatable withrespect to the center plate 20.

A bearing 18 a for a first eccentric shaft portion (crank pin endportion rolling bearing) and a bearing 18 b for a second eccentric shaftportion (crank pin end portion rolling bearing), which are angular ballbearings, are provided at both ends of the eccentric shaft portion 15 b,respectively. As a result, the eccentric shaft portion 15 b is rotatablewith respect to the first side plate 27 and the second side plate 30.

The crank pin 15 and the respective bearings 16, 18 a, and 18 b are usedas synchronization drive mechanisms transmitting the drive force of themotor 5 to the driven-side scroll member 90 such that both scrollmembers 70 and 90 perform revolving and orbiting motions insynchronization.

It is preferable that a plurality of the synchronization drivemechanisms provided with the crank pin 15 are provided. For example,three synchronization drive mechanisms are provided at equal angulargaps around the drive-side rotational axis CL3.

The co-rotating scroll compressor 1 configured as described aboveoperates as follows.

The drive shaft 6 is rotated around the drive-side rotational axis CL1by the motor 5, and then the center plate 20 also rotates via the shank20 a connected to the drive shaft 6. By the center plate 20 rotating,the drive-side scroll member 70 connected via the fixing portion 20 brotates around the drive-side rotational axis CL1. The drive forcetransmitted to the center plate 20 is transmitted from the first sideplate 27 and the second side plate 30 to the driven-side scroll member90 via the crank pin 15 as a synchronization drive mechanism and thedriven-side scroll member 90 rotates around the driven-side rotationalaxis CL2. At this time, the crank pin 15 rotates with respect to thecenter plate 20 and both side plates via the respective bearings 16, 18a, and 18 b, and thus both scroll members 70 and 90 relatively performthe revolving and orbiting motions.

By both scroll members 70 and 90 performing the revolving and orbitingmotions, the air suctioned from the intake port of the housing 3 issuctioned from the outer peripheral sides of both scroll members 70 and90 and taken into the compression chamber formed by both scroll members70 and 90. Then, the compression chamber formed by the first drive-sidewall body 71 b and the first driven-side wall body 91 b and thecompression chamber formed by the second drive-side wall body 72 b andthe second driven-side wall body 92 b are separately compressed. The airis compressed as the volume of each compression chamber decreases with amovement to the center side. The air compressed by the first drive-sidewall body 71 b and the first driven-side wall body 91 b passes throughthe through-hole 90 h formed in the driven-side end plate 90 a andmerges with the air compressed by the second drive-side wall body 72 band the second driven-side wall body 92 b, and the merged air isdischarged from the discharge port 3 d of the housing 3 to the outsidethrough the discharge port 72 d.

The present embodiment has the following action and effect.

The first side plate 27 and the second side plate 30 are provided on therotational axis direction CL1 side and the rotational axis direction CL2side with respect to the drive-side scroll member 70 and the driven-sidescroll member 90 and the center plate 20 is provided between the sideplates 27 and 30. The crank pin 15 and the respective bearings 16, 18 a,and 18 b are provided as the synchronization drive mechanisms betweenboth side plates 27 and 30 and the center plate 20. Since the sideplates 27 and 30 and the center plate 20 as members separate from bothscroll members 70 and 90 are provided with the synchronization drivemechanisms as described above, heating attributable to the compressionheat from the scroll members 70 and 90 can be decreased as compared witha case where a synchronization drive mechanism is provided with respectto end plates of the scroll members 70 and 90 and the life of thesynchronization drive mechanisms can be extended.

A load is applied to the crank pin 15 from the center plate 20 and theside plates 27 and 30 on both sides thereof, and thus the moment aroundthe cylindrical portion 15 a of the crank pin 15 can be canceled and thelife of the synchronization drive mechanisms can be extended.

The synchronization drive mechanisms are disposed by both side plates 27and 30 and the center plate 20 being provided on the rotational axis CL1direction side and the rotational axis CL2 direction side, and thusdiameter reduction can be achieved as compared with a case where asynchronization drive mechanism is provided on radial direction sides ofthe scroll members 70 and 90.

Although the crank pin 15 is used as a synchronization drive mechanismin the present embodiment, the present invention is not limited thereto.For example, a pin ring mechanism that a pin member and a ring memberconstitute may be used.

Second Embodiment

Next, a second embodiment of the present invention will be described.The present embodiment relates to a synchronization drive mechanismprovided with the crank pin 15 described in the first embodiment.Accordingly, the overall configuration of the co-rotating scrollcompressor 1 is similar to that of the first embodiment and will not bedescribed below.

As illustrated in FIG. 5, in end portions 15 c on both sides of theeccentric shaft portion 15 b of the crank pin 15, small-diameterportions 15 d smaller in diameter than a central portion 15 e areprovided at the positions where the inner rings of the bearings 18 a and18 b for the eccentric shaft portions are attached. A step section 15 jbetween the central portion 15 e and the small-diameter portion 15 d isprovided with an O-ring (urging member) 19.

The O-ring 19 urges the inner rings of the bearings 18 a and 18 b forthe eccentric shaft portions in the eccentric axis CL3 direction towardthe leading edge of the crank pin 15.

In FIG. 5, reference sign 41 denotes a seal plate for sealing alubricant and reference sign 42 denotes a stopper ring for fixing theseal plate 41.

The present embodiment has the following action and effect.

The O-ring 19 is provided between the inner rings of the bearings 18 aand 18 b for the eccentric shaft portions and the eccentric shaftportion 15 b of the crank pin 15 and the O-ring 19 urges the inner ringsin the eccentric axis CL3 direction toward the leading edge of theeccentric shaft portion 15 b. The O-ring 19 urges the inner rings of thebearings 18 a and 18 b for the eccentric shaft portions toward theleading edge, and thus an outer ring is pressed against the side plates27 and 30 via the balls (rolling bodies) of the bearings 18 a and 18 bfor the eccentric shaft portions. As a result, the bearings 18 a and 18b for the eccentric shaft portions are put into a state where a preloadis applied between the eccentric shaft portion 15 b of the crank pin 15and the side plates 27 and 30, it is possible to prevent slippingbetween the ball and the inner ring and slipping between the inner ringand the eccentric shaft portion 15 b, and the life of thesynchronization drive mechanism can be extended.

Modification Example 1

The configuration illustrated in FIG. 6 may be adopted, instead of oralong with the present embodiment, as means for applying a preload tothe bearings 18 a and 18 b for the eccentric shaft portions.

FIG. 6 illustrates a state where the second side plate 30 is yet to befixed to the first side plate 27 by the bolt 31. In this state, a gap tis formed between the first side plate 27 and the leading edge of afixing portion 30 b of the second side plate 30. In this manner, the gapdetermined by both side plates 27 and 30 being fastened by means of thebolt 31 is kept smaller than the gap between both side plates 27 and 30determined by the crank pin 15 and the respective bearings 16, 18 a, and18 b. As a result, the gap between the side plates 27 and 30 is narrowedwhen the second side plate 30 is fastened to the first side plate 27 bymeans of the bolt 31 and a preload can be applied in the eccentric axisCL3 direction to the bearings 18 a and 18 b for the eccentric shaftportions.

Modification Example 2

The configuration illustrated in FIG. 7 may be adopted, instead of oralong with the present embodiment, as means for preventing the innerrings of the bearings 18 a and 18 b for the eccentric shaft portionsfrom slipping.

As illustrated in FIG. 7, an O-ring (elastic body) 22 is providedbetween the inner peripheral surface of the inner ring of the bearing 18a for the first eccentric shaft portion and the outer peripheral surfaceof the eccentric shaft portion 15 b. The O-ring 22 urges the inner ringof the bearing 18 a for the first eccentric shaft portion to the radialouter side about the eccentric axis CL3 by means of the reaction forceresulting from deformation of the O-ring 22. As a result, slippingbetween the eccentric shaft portion 15 b and the inner ring can beprevented.

The bearing 18 b for the second eccentric shaft portion may be providedwith the O-ring 22.

Third Embodiment

Next, a third embodiment of the present invention will be described. Thepresent embodiment is different from the first embodiment in terms ofthe fixing portion 20 b fixing the center plate 20 to the drive-sidescroll member 70. The third embodiment is similar to the firstembodiment regarding the other points, and thus the points will not bedescribed below.

As illustrated in FIG. 8, a fixing portion 20 b′ of the center plate 20is positioned on the drive-side rotational axis CL1 side with respect toa fixing portion 27 a of the first side plate 27 and the fixing portion30 b of the second side plate 30. The fixing portion 20 b′ of the centerplate 20 has a structure in which a resinous shaft portion 40 made ofresin is interposed. The other part of the center plate 20 is metallicand made of aluminum alloy or iron.

The fixing portion 27 a of the first side plate 27 and the fixingportion 30 b of the second side plate 30 have a metallic structurewithout resin portion interposition.

The present embodiment has the following action and effect.

The structure in which the resinous shaft portion 40 is interposed isbecause the temperature of the fixing portion 20 b′ of the center plate20, which is positioned radially inward of the centers of the scrollmembers 70 and 90, tends to rise due to compression heat. As a result,it is possible to achieve life extension by suppressing a rise in thetemperature of the synchronization drive mechanism provided with thecrank pin 15.

The metallic structure without resin portion interposition is because arise in temperature attributable to compression heat has little effecton the fixing portion 27 a of the first side plate 27 and the fixingportion 30 b of the second side plate 30, which are positioned radiallyoutward of the centers of the scroll members 70 and 90. As a result, thefixing portions 27 a and 30 b can be accurately assembled by means ofmetal, and thus the synchronization drive mechanism can be accuratelypositioned, phase shift reduction can be achieved between the drive-sidescroll member 70 and the driven-side scroll member 90, and compressionperformance improvement can be achieved.

Fourth Embodiment

Hereinafter, a fourth embodiment of the present invention will bedescribed with reference to the drawings including FIG. 9.

FIG. 9 illustrates the co-rotating scroll compressor 1. The co-rotatingscroll compressor 1 can be used as a turbocharger compressing combustionair (a fluid) supplied to an internal combustion engine such as avehicular engine, a compressor for supplying compressed air to anelectrode of a fuel cell, or a compressor for supplying compressed airused for a braking device of a vehicle such as a railway vehicle.

The co-rotating scroll compressor 1 is provided with the housing 3, themotor (drive unit) 5 accommodated on one end side of the housing 3, andthe drive-side scroll member 70 and the driven-side scroll member 90accommodated on the other end side of the housing 3.

The housing 3 has a substantially cylindrical shape and is provided withthe motor accommodation portion 3 a accommodating the motor 5 and thescroll accommodation portion 3 b accommodating the scroll members 70 and90.

The discharge port 3 d for discharging compressed air is formed in anend portion of the scroll accommodation portion 3 b. The housing 3 isprovided with an air intake port (not illustrated in FIG. 9) suctioningair.

The motor 5 is driven by power being supplied from a power supply source(not illustrated). The rotation of the motor 5 is controlled by acommand from a control unit (not illustrated). The stator 5 a of themotor 5 is fixed to the inner peripheral side of the housing 3. Therotor 5 b of the motor 5 rotates around the drive-side rotational axisCL1. The drive shaft 6 extending on the drive-side rotational axis CL1is connected to the rotor 5 b. The drive shaft 6 is connected to a driveshaft portion 71 d fixed to the first drive-side scroll part 71 of thedrive-side scroll member 70.

The drive-side bearing 11 rotatably supporting the drive shaft 6 isprovided at the front end (left end in FIG. 9) of the drive shaft 6. Therear end bearing 17 rotatably supporting the drive shaft 6 between thehousing 3 and the rear end bearing 17 is provided at the rear end (rightend in FIG. 9) of the drive shaft 6, that is, in the end portion of thedrive shaft 6 that is on the side opposite to the drive-side scrollmember 70.

The drive-side scroll member 70 is provided with the first drive-sidescroll part 71 on the motor 5 side and the second drive-side scroll part72 on the discharge port 3 d side.

The first drive-side scroll part 71 is provided with the firstdrive-side end plate 71 a and the first drive-side wall body 71 b.

The first drive-side end plate 71 a extends in a direction orthogonal tothe drive-side rotational axis CL1. The drive shaft portion 71 dextending on and along the drive-side rotational axis CL1 is fixed tothe rotation center of the first drive-side end plate 71 a.

The center plate 20 is fixed to the drive shaft portion 71 d. The centerplate 20 extends in parallel with the first drive-side end plate 71 a.

The first drive-side end plate 71 a is substantially disk-shaped in planview. As illustrated in FIG. 10, the three spiral first drive-side wallbodies 71 b, that is, the spiral first drive-side wall bodies 71 b inthe form of three flights are provided on the first drive-side end plate71 a. The first drive-side wall bodies 71 b in the form of three flightsare disposed at equal gaps around the drive-side rotational axis CL1.The first drive-side wall body 71 b may be one, two, or four or more inthe number of flights.

As illustrated in FIG. 9, the second drive-side scroll part 72 isprovided with the second drive-side end plate 72 a and the seconddrive-side wall body 72 b. The second drive-side wall body 72 b is inthe form of three flights similarly to the first drive-side wall body 71b (see FIG. 10) described above. The second drive-side wall body 72 bmay be one, two, or four or more in the number of flights.

The second drive-side shaft portion 72 c extending in the drive-siderotational axis CL1 direction is connected to the second drive-side endplate 72 a. The second drive-side shaft portion 72 c is providedrotatably with respect to the housing 3 via the second drive-sidebearing 14, which is a ball bearing. The second drive-side end plate 72a is provided with the discharge port 72 d, which is along thedrive-side rotational axis CL1.

The two seal members 26 are provided between the second drive-side shaftportion 72 c and the housing 3 and on the leading edge side (left sidein FIG. 9) of the second drive-side shaft portion 72 c beyond the seconddrive-side bearing 14. The two seal members 26 and the second drive-sidebearing 14 are disposed at predetermined gaps in the drive-siderotational axis CL1 direction. Enclosed between the two seal members 26is a lubricant that is grease such as a semi-solid lubricant. The sealmember 26 may be one in number. In this case, the lubricant is enclosedbetween the seal member 26 and the second drive-side bearing 14.

The first drive-side scroll part 71 and the second drive-side scrollpart 72 are fixed in a state where the leading edges (free ends) of thewall bodies 71 b and 72 b face each other. The first drive-side scrollpart 71 and the second drive-side scroll part 72 are fixed by the bolt31, which is fastened to the flange portions 73 provided at a pluralityof places in the circumferential direction so as to protrude to theradial outer side.

In the driven-side scroll member 90, the driven-side end plate 90 a ispositioned substantially at the center in the axial direction(horizontal direction in the drawing). The through-hole 90 h is formedat the center of the driven-side end plate 90 a and compressed air flowsto the discharge port 72 d.

The first driven-side wall body 91 b and the second driven-side wallbody 92 b are provided on both sides of the driven-side end plate 90 a,respectively. The first driven-side wall body 91 b installed on themotor 5 side from the driven-side end plate 90 a meshes with the firstdrive-side wall body 71 b of the first drive-side scroll part 71 and thesecond driven-side wall body 92 b installed on the discharge port 3 dside from the driven-side end plate 90 a meshes with the seconddrive-side wall body 72 b of the second drive-side scroll part 72.

The three first driven-side wall bodies 91 b, that is, the firstdriven-side wall bodies 91 b in the form of three flights are providedas illustrated in FIG. 11. The driven-side wall bodies 91 b in the formof three flights are disposed at equal gaps around the driven-siderotational axis CL2. The second driven-side wall body 92 b is similar inconfiguration. Each of the driven-side wall bodies 91 b and 92 b may beone, two, or four or more in the number of flights.

The support member 33 is provided on the discharge port 3 d side (leftside in FIG. 9) of the driven-side scroll member 90. The support member33 is fixed by the bolt 25 to the leading edge (free end) of the seconddriven-side wall body 92 b.

The shank 35 a for the support member is provided on the central axisside of the support member 33 and the shank 35 a for the support memberis fixed to the housing 3 via the bearing 38 for the second supportmember, which is an angular ball bearing. As a result, the driven-sidescroll member 90 rotates around the driven-side rotational axis CL2 viathe support member 33.

The first side plate 27 is provided on the motor 5 side (right side inFIG. 9) of the driven-side scroll member 90. The first side plate 27 isfixed by the bolt 28 to the leading edge (free end) of the firstdriven-side wall body 91 b. Formed at the rotation center of the firstside plate is a hole portion 27 h for the first side plate forpenetration by the drive shaft portion 71 d.

The second side plate 30 is provided at a predetermined gap on the motor5 side of the first side plate 27. The second side plate 30 is fixed bya bolt 34 to the first side plate 27. Formed at the rotation center ofthe second side plate 30 is a hole portion 30 h for the second sideplate for penetration by the drive shaft portion 71 d.

The shank 30 a for the second side plate is provided on the central axisside of the second side plate 30 and the shank 30 a for the second sideplate is fixed to the housing 3 via the bearing 32 for the second sideplate, which is an angular ball bearing. As a result, the driven-sidescroll member 90 rotates around the driven-side rotational axis CL2 viathe second side plate 30 and the first side plate 27.

A first protruding wall portion 27 b protruding toward the second sideplate 30 is provided on the outer peripheral side end surface of thefirst side plate 27. A second protruding wall portion 30 c protrudingtoward the first side plate 27 is provided on the outer peripheral sideend surface of the second side plate 30. The protruding wall portions 27b and 30 c constitute a peripheral wall portion by being attached toeach other and fixed in a liquid-tight state. As a result, the centerplate 20 disposed between the first side plate 27 and the second sideplate 30 is accommodated in a space S surrounded by both protruding wallportions 27 b and 30 c as illustrated in FIG. 12.

As illustrated in FIG. 9, the crank pin 15 is provided between the firstand second side plates 27 and 30 and the center plate 20. The crank pin15 has the cylindrical portion 15 a at the center and the eccentricshaft portion 15 b, which has an eccentric axis eccentric to the centralaxis of the cylindrical portion 15 a.

Provided on the outer periphery of the cylindrical portion 15 a is thebearing 16 for the cylindrical portion, which is a ball bearing. As aresult, the cylindrical portion 15 a is rotatable with respect to thecenter plate 20. A lubricant such as grease is enclosed in the bearing16 for the cylindrical portion.

The bearing 18 a for the first eccentric shaft portion (crank pin endportion rolling bearing 18 a) and the bearing 18 b for the secondeccentric shaft portion (crank pin end portion rolling bearing 18 b),which are ball bearings, are provided at both ends of the eccentricshaft portion 15 b, respectively. As a result, the eccentric shaftportion 15 b is rotatable with respect to the first side plate 27 andthe second side plate 30. A lubricant such as grease is enclosed in eachof the bearings 18 a and 18 b for the eccentric shaft portions.

The crank pin 15 and the respective bearings 16, 18 a, and 18 b are usedas synchronization drive mechanisms transmitting a drive force from thedrive shaft portion 71 d to the driven-side scroll member 90 such thatboth scroll members 70 and 90 perform revolving and orbiting motions insynchronization.

It is preferable that a plurality of the synchronization drivemechanisms provided with the crank pin 15 are provided. For example,three synchronization drive mechanisms are provided at equal angulargaps around the drive-side rotational axis CL3 (see FIG. 12).

The co-rotating scroll compressor 1 configured as described aboveoperates as follows.

The drive shaft 6 is rotated around the drive-side rotational axis CL1by the motor 5, and then the center plate 20 as well as the drive-sidescroll member 70 rotates around the drive-side axis CL1 via the driveshaft portion 71 d connected to the drive shaft 6. By the center plate20 rotating, the drive force transmitted to the center plate istransmitted from the first side plate 27 and the second side plate 30 tothe driven-side scroll member 90 via the crank pin 15 as asynchronization drive mechanism and the driven-side scroll member 90rotates around the driven-side rotational axis CL2. At this time, thecrank pin 15 rotates with respect to the center plate 20 and both sideplates via the respective bearings 16, 18 a, and 18 b, and thus bothscroll members 70 and 90 relatively perform the revolving and orbitingmotions.

By both scroll members 70 and 90 performing the revolving and orbitingmotions, the air suctioned from the intake port of the housing 3 issuctioned from the outer peripheral sides of both scroll members 70 and90 and taken into the compression chamber formed by both scroll members70 and 90. Then, the compression chamber formed by the first drive-sidewall body 71 b and the first driven-side wall body 91 b and thecompression chamber formed by the second drive-side wall body 72 b andthe second driven-side wall body 92 b are separately compressed. The airis compressed as the volume of each compression chamber decreases with amovement to the center side. The air compressed by the first drive-sidewall body 71 b and the first driven-side wall body 91 b passes throughthe through-hole 90 h formed in the driven-side end plate 90 a andmerges with the air compressed by the second drive-side wall body 72 band the second driven-side wall body 92 b, and the merged air isdischarged from the discharge port 3 d of the housing 3 to the outsidethrough the discharge port 72 d.

The present embodiment has the following action and effect.

The first side plate 27 and the second side plate 30 are provided on therotational axis CL1 direction side and the rotational axis CL2 directionside with respect to the drive-side scroll member 70 and the driven-sidescroll member 90 and the center plate 20 is provided between the sideplates 27 and 30. The crank pin 15 and the respective bearings 16, 18 a,and 18 b are provided as the synchronization drive mechanisms betweenboth side plates 27 and 30 and the center plate 20. Further, the firstprotruding wall portion 27 b and the second protruding wall portion 30 care provided between the first side plate 27 and the second side plate30 as the peripheral wall portion surrounding the outer peripheral sideof the center plate 20. As a result, even when the lubricant supplied tothe synchronization drive mechanism (specifically, each of the bearings16, 18 a, and 18 b) is moved to the outer peripheral side by acentrifugal force, the lubricant can be held on the inner peripheralside of the liquid-tight peripheral wall portion, and thus aninsufficient lubrication of the synchronization drive mechanism can beavoided and life extension can be achieved.

In addition, it is possible to prevent the compressed air from beingcontaminated by preventing lubricant leakage.

Although the peripheral wall portion is constituted by means of thefirst protruding wall portion 27 b and the second protruding wallportion 30 c in the present embodiment, the present invention is notlimited thereto. The peripheral wall portion may be provided so as tosurround the outer periphery of the center plate 20. For example, thefirst protruding wall portion 27 b may constitute the peripheral wallportion alone or the second protruding wall portion 30 c may constitutethe peripheral wall portion alone. In addition, the peripheral wallportion may be configured by means of a member other than the sideplates 27 and 30.

Although the crank pin 15 is used as a synchronization drive mechanismin the present embodiment, the present invention is not limited theretoand the synchronization drive mechanism may be any synchronization drivemechanism requiring lubricant supply. For example, a pin ring mechanismthat a pin member and a ring member constitute may be used.

Fifth Embodiment

Next, a fifth embodiment of the present invention will be described. Thepresent embodiment differs from the fourth embodiment in that a sealmember is provided with respect to the side plates 27 and 30.Accordingly, the overall configuration of the co-rotating scrollcompressor 1 is similar to that of the fourth embodiment and will not bedescribed below.

As illustrated in FIG. 13, a first seal member 43 is provided betweenthe first side plate 27 and the drive shaft portion 71 d. A boots sealor a labyrinth seal can be adopted as the first seal member 43.

A second seal member 44 is provided between end surfaces of the secondside plate 30 and the center plate 20. An annular and resinous tip sealcan be adopted as the second seal member 44. The second seal member 44is accommodated in a circumferential groove formed in the end surface ofthe second side plate 30. The second seal member 44 may be installed onthe center plate 20 side by means of circumferential groove formation inthe center plate 20.

The present embodiment has the following action and effect.

Sealing is performed between the first side plate 27 and the drive shaftportion 71 d by the first seal member 43 being provided. As a result, itis possible to prevent lubricant leakage from the space between thefirst side plate 27 and the drive shaft portion 71 d. The first sealmember 43 may be provided between the second side plate 30 and the driveshaft portion 71 d.

The second seal member 44 is provided between the second side plate 30and the center plate 20. As a result, it is possible to preventlubricant leakage from the space between the second side plate 30 andthe drive shaft portion 71 d. The second seal member 44 may be providedbetween the first side plate 27 and the center plate 20.

Sixth Embodiment

Next, a sixth embodiment of the present invention will be described. Thepresent embodiment differs from the fourth embodiment in that the sideplates 27 and 30 are the drive side and the center plate 20 is thedriven side. The sixth embodiment is similar to the fourth embodimentregarding the other points, and thus the points will not be describedbelow.

As illustrated in FIG. 14, the drive shaft 6 (see FIG. 9) of the motor 5is connected to a drive shaft portion 30 d protruding to the motor 5side from the rotation center of the second side plate 30. Accordingly,the drive force from the motor 5 is transmitted from the second sideplate 30 to a drive-side scroll member 50 via the first side plate 27.In other words, the driven-side scroll member 90 of the fourthembodiment is the drive side.

A drive force is transmitted from both side plates 27 and 30 to thecenter plate 20 via the synchronization drive mechanism provided withthe crank pin 15. A driven shaft portion 61 d is fixed to the centerplate 20. The driven shaft portion 61 d is provided at the rotationcenter of a first driven-side end plate 61 a of a driven-side scrollmember 60. Accordingly, the drive-side scroll member 70 of the fourthembodiment is the driven side.

As in the fourth embodiment, the first protruding wall portion 27 b ofthe first side plate 27 and the second protruding wall portion 30 c ofthe second side plate 30 constitute a peripheral wall portion.Accordingly, the configuration, action, and effect thereof will not bedescribed below.

Unlike in the fourth embodiment, the rotation center region of thesecond side plate 30 is not provided with a hole portion (the holeportion 30 h for the second side plate: see FIG. 9). The rotation centerregion of the second side plate 30 is closed by a wall portion.

The present embodiment has the following action and effect.

The drive shaft portion 30 d is provided with respect to the rotationcenter of the second side plate 30. As a result, a drive force istransmitted from the motor 5 to the drive-side scroll member 50 via thefirst side plate 27 and the second side plate 30.

The drive force transmitted from both side plates 27 and 30 via thesynchronization drive mechanism is guided from the center plate 20 tothe driven-side scroll member 60 by the center plate 20 being fixed tothe driven shaft portion 61 d connected to the rotation center of thefirst driven-side end plate 61 a of the driven-side scroll member 60.The driven shaft portion 61 d is disposed so as to pass through the holeportion 27 h for the first side plate formed in the first side plate 27.Since a drive force is transmitted from the center plate 20 to thedriven shaft portion 61 d via the synchronization drive mechanism, thereis no need to form a hole portion for penetration by the driven shaftportion 61 d in the rotation center region of the second side plate 30.Accordingly, it is possible to adopt the second side plate 30 that has arotation center region closed by a wall portion, and thus lubricantleakage from the rotation center of the second side plate 30 can beprevented.

In addition, there is no need to provide a bearing rotatably supportingthe driven shaft portion 61 d. Accordingly, the drive-side bearing 11(see FIG. 9) of the fourth embodiment can be omitted and the number ofcomponents can be reduced.

Seventh Embodiment

Hereinafter, a seventh embodiment of the present invention will bedescribed with reference to the drawings including FIG. 15.

FIG. 15 illustrates the co-rotating scroll compressor 1. The co-rotatingscroll compressor 1 can be used as a turbocharger compressing combustionair (a fluid) supplied to an internal combustion engine such as avehicular engine, a compressor for supplying compressed air to an airelectrode of a fuel cell, or a compressor for supplying compressed airused for a braking device of a vehicle such as a railway vehicle.

The co-rotating scroll compressor 1 is provided with the housing 3, themotor (drive unit) 5 accommodated on one end side of the housing 3, andthe drive-side scroll member 70 and the driven-side scroll member 90accommodated on the other end side of the housing 3.

The housing 3 has a substantially cylindrical shape and is provided withthe motor accommodation portion 3 a accommodating the motor 5 and thescroll accommodation portion 3 b accommodating the scroll members 70 and90.

The discharge port 3 d for discharging compressed air is formed in anend portion of the scroll accommodation portion 3 b. The housing 3 isprovided with an air intake port (not illustrated in FIG. 15) suctioningair.

The motor 5 is driven by power being supplied from a power supply source(not illustrated). The rotation of the motor 5 is controlled by acommand from a control unit (not illustrated). The stator 5 a of themotor 5 is fixed to the inner peripheral side of the housing 3. Therotor 5 b of the motor 5 rotates around the drive-side rotational axisCL1. The drive shaft 6 extending on the drive-side rotational axis CL1is connected to the rotor 5 b. The drive shaft 6 is connected to thedrive shaft portion 71 d fixed to the first drive-side scroll part 71 ofthe drive-side scroll member 70.

The drive-side bearing 11 rotatably supporting the drive shaft 6 isprovided at the front end (left end in FIG. 15) of the drive shaft 6. Arear end bearing 24 rotatably supporting the drive shaft 6 between thehousing 3 and the rear end bearing 24 is provided at the rear end (rightend in FIG. 15) of the drive shaft 6, that is, in the end portion of thedrive shaft 6 that is on the side opposite to the drive-side scrollmember 70.

The drive-side scroll member 70 is provided with the first drive-sidescroll part 71 on the motor 5 side and the second drive-side scroll part72 on the discharge port 3 d side.

The first drive-side scroll part 71 is provided with the firstdrive-side end plate 71 a and the first drive-side wall body 71 b.

The first drive-side end plate 71 a extends in a direction orthogonal tothe drive-side rotational axis CL1. The drive shaft portion 71 dextending on and along the drive-side rotational axis CL1 is fixed tothe rotation center of the first drive-side end plate 71 a.

The center plate 20 is fixed to the drive shaft portion 71 d. The centerplate 20 extends in parallel with the first drive-side end plate 71 a.

The first drive-side end plate 71 a is substantially disk-shaped in planview. As illustrated in FIG. 16, the three spiral first drive-side wallbodies 71 b, that is, the spiral first drive-side wall bodies 71 b inthe form of three flights are provided on the first drive-side end plate71 a. The first drive-side wall bodies 71 b in the form of three flightsare disposed at equal gaps around the drive-side rotational axis CL1.The first drive-side wall body 71 b may be one, two, or four or more inthe number of flights.

As illustrated in FIG. 15, the second drive-side scroll part 72 isprovided with the second drive-side end plate 72 a and the seconddrive-side wall body 72 b. The second drive-side wall body 72 b is inthe form of three flights similarly to the first drive-side wall body 71b (see FIG. 16) described above. The second drive-side wall body 72 bmay be one, two, or four or more in the number of flights.

The second drive-side shaft portion 72 c extending in the drive-siderotational axis CL1 direction is connected to the second drive-side endplate 72 a. The second drive-side shaft portion 72 c is providedrotatably with respect to the housing 3 via the second drive-sidebearing 14, which is a ball bearing. The second drive-side end plate 72a is provided with the discharge port 72 d, which is along thedrive-side rotational axis CL1.

The two seal members 26 for a second drive shaft portion are providedbetween the second drive-side shaft portion 72 c and the housing 3 andon the leading edge side (left side in FIG. 15) of the second drive-sideshaft portion 72 c beyond the second drive-side bearing 14. The two sealmembers 26 for the second drive shaft portion and the second drive-sidebearing 14 are disposed at predetermined gaps in the drive-siderotational axis CL1 direction. Enclosed between the two seal members 26for the second drive shaft portion is a lubricant that is grease such asa semi-solid lubricant. The seal member 26 for the second drive shaftportion may be one in number. In this case, the lubricant is enclosedbetween the seal member 26 for the second drive shaft portion and thesecond drive-side bearing 14.

The first drive-side scroll part 71 and the second drive-side scrollpart 72 are fixed in a state where the leading edges (free ends) of thewall bodies 71 b and 72 b face each other. The first drive-side scrollpart 71 and the second drive-side scroll part 72 are fixed by the bolt31, which is fastened to the flange portions 73 provided at a pluralityof places in the circumferential direction so as to protrude to theradial outer side.

In the driven-side scroll member 90, the driven-side end plate 90 a ispositioned substantially at the center in the axial direction(horizontal direction in the drawing). The through-hole 90 h is formedat the center of the driven-side end plate 90 a and compressed air flowsto the discharge port 72 d.

The first driven-side wall body 91 b and the second driven-side wallbody 92 b are provided on both sides of the driven-side end plate 90 a,respectively. The first driven-side wall body 91 b installed on themotor 5 side from the driven-side end plate 90 a meshes with the firstdrive-side wall body 71 b of the first drive-side scroll part 71 and thesecond driven-side wall body 92 b installed on the discharge port 3 dside from the driven-side end plate 90 a meshes with the seconddrive-side wall body 72 b of the second drive-side scroll part 72.

The three first driven-side wall bodies 91 b, that is, the firstdriven-side wall bodies 91 b in the form of three flights are providedas illustrated in FIG. 17. The driven-side wall bodies 91 b in the formof three flights are disposed at equal gaps around the driven-siderotational axis CL2. The second driven-side wall body 92 b is similar inconfiguration. Each of the driven-side wall bodies 91 b and 92 b may beone, two, or four or more in the number of flights.

The support member 33 is provided on the discharge port 3 d side (leftside in FIG. 15) of the driven-side scroll member 90. The support member33 is fixed by the bolt 25 to the leading edge (free end) of the seconddriven-side wall body 92 b.

The shank 35 a for the support member is provided on the central axisside of the support member 33 and the shank 35 a for the support memberis fixed to the housing 3 via the bearing 38 for the second supportmember, which is a ball bearing. As a result, the driven-side scrollmember 90 rotates around the driven-side rotational axis CL2 via thesupport member 33.

The first side plate 27 is provided on the motor 5 side (right side inFIG. 15) of the driven-side scroll member 90. The first side plate 27 isfixed by the bolt 28 to the leading edge (free end) of the firstdriven-side wall body 91 b. Formed at the rotation center of the firstside plate 27 is the hole portion 27 h for the first side plate forpenetration by the drive shaft portion 71 d.

The second side plate 30 is provided at a predetermined gap on the motor5 side of the first side plate 27. The second side plate 30 is fixed bythe bolt 34 to the first side plate 27. Formed at the rotation center ofthe second side plate 30 is the hole portion 30 h for the second sideplate for penetration by the drive shaft portion 71 d.

The shank 30 a for the second side plate is provided on the central axisside of the second side plate 30 and the shank 30 a for the second sideplate is fixed to the housing 3 via the bearing 32 for the second sideplate, which is a ball bearing. As a result, the driven-side scrollmember 90 rotates around the driven-side rotational axis CL2 via thesecond side plate 30 and the first side plate 27. The closed space thatis formed between the second side plate 30 and the first side plate 27is supplied with a lubricant such as oil and grease, and a slidingportion is lubricated as a result.

The first protruding wall portion 27 b protruding toward the second sideplate 30 is provided on the outer peripheral side end surface of thefirst side plate 27. The second protruding wall portion 30 c protrudingtoward the first side plate 27 is provided on the outer peripheral sideend surface of the second side plate 30. The protruding wall portions 27b and 30 c constitute a peripheral wall portion by being attached toeach other and fixed in a liquid-tight state. As a result, the centerplate 20 disposed between the first side plate 27 and the second sideplate 30 is accommodated in the space S surrounded by both protrudingwall portions 27 b and 30 c as illustrated in FIG. 18.

As illustrated in FIG. 15, the pin ring mechanism (synchronization drivemechanism) 15 is provided between the first and second side plates 27and 30 and the center plate 20. The pin ring mechanism 15 is providedwith a round bar-shaped pin 45 and a rolling bearing (ring) 46, whichguides the pin 45 by the inner peripheral surface of the rolling bearing46 abutting against the outer periphery of the pin 45.

As illustrated in FIG. 18, three pin ring mechanisms 15 are provided atequal angular gaps around the rotation center of the center plate 20.The pin ring mechanism 15 may be four or more in number.

FIG. 19 is an enlarged view of the part around the pin ring mechanism15.

One end (the left end) of the pin 45 is press-fitted and fixed to thefirst side plate 27 and the other end (right end) of the pin 45 ispress-fitted and fixed to the second side plate 30. The longitudinalcentral portion of the pin 45 abuts against the inner peripheral surfaceof an inner ring 46 b of the rolling bearing 46.

The rolling bearing 46, which is a ball bearing, is fitted in a holeportion formed in the center plate 20. The rolling bearing 46 isprovided with an outer ring 46 a, the inner ring 46 b, a plurality ofballs (rolling members) 46 c, and a holder (not illustrated) holdingeach ball 46 c. A lubricant such as grease is enclosed in the rollingbearing 46.

The pin ring mechanism 15 is used as a synchronization drive mechanismtransmitting a drive force from the drive shaft portion 71 d to thedriven-side scroll member 90 such that both scroll members 70 and 90relatively perform revolving and orbiting motions in synchronization.

The co-rotating scroll compressor 1 configured as described aboveoperates as follows.

The drive shaft 6 is rotated around the drive-side rotational axis CL1by the motor 5, and then the center plate 20 as well as the drive-sidescroll member 70 rotates around the drive-side axis CL1 via the driveshaft portion 71 d connected to the drive shaft 6. By the center plate20 rotating, the drive force transmitted to the center plate istransmitted from the first side plate 27 and the second side plate 30 tothe driven-side scroll member 90 via the pin ring mechanism 15 as asynchronization drive mechanism and the driven-side scroll member 90rotates around the driven-side rotational axis CL2. At this time, thepin ring mechanism 15 causes both scroll members 70 and 90 to relativelyperform the revolving and orbiting motions.

By both scroll members 70 and 90 performing the revolving and orbitingmotions, the air suctioned from the intake port of the housing 3 issuctioned from the outer peripheral sides of both scroll members 70 and90 and taken into the compression chamber formed by both scroll members70 and 90. Then, the compression chamber formed by the first drive-sidewall body 71 b and the first driven-side wall body 91 b and thecompression chamber formed by the second drive-side wall body 72 b andthe second driven-side wall body 92 b are separately compressed. The airis compressed as the volume of each compression chamber decreases with amovement to the center side. The air compressed by the first drive-sidewall body 71 b and the first driven-side wall body 91 b passes throughthe through-hole 90 h formed in the driven-side end plate 90 a andmerges with the air compressed by the second drive-side wall body 72 band the second driven-side wall body 92 b, and the merged air isdischarged from the discharge port 3 d of the housing 3 to the outsidethrough the discharge port 72 d.

The present embodiment has the following action and effect.

The pin ring mechanism 15 provided with the round bar-shaped pin 45 andthe rolling bearing 46 is adopted as a synchronization drive mechanism.As a result, it is possible to realize the synchronization drivemechanism without adopting a crank pin mechanism, and thus it ispossible to achieve cost reduction without a complex configurationcaused by a large number of bearings being adopted as in the case ofcrank pin mechanisms.

The pin 45 is press-fitted and fixed to the side plates 27 and 30, andthus the pin 45 can be used as a positioning pin for both side plates 27and 30.

Both ends of the pin 45 are fixed to both side plates 27 and 30 and thecentral portion of the pin 45 abuts against the inner peripheral surfaceof the rolling bearing 46. Accordingly, inclination of the inner ring 46b of the rolling bearing 46 can be prevented, an oblique movement of theball 46 c can be prevented, and the life of the synchronization drivemechanism can be extended.

Modification Example 1

The present embodiment can be modified as follows. As illustrated inFIG. 20, in a pin ring mechanism 15A of the present modificationexample, one end (the left end) of the pin 45 is press-fitted and fixedto the first side plate 27 as in the seventh embodiment and the otherend (right end) of the pin 45 is fixed to the second side plate 30 viaan O-ring (elastic body) 47.

The present modification example has the following action and effect.

One end of the pin 45 is press-fitted and fixed to the first side plate27 and the other end of the pin 45 is fixed to the second side plate 30via the O-ring 47. As a result, both ends of the pin 45 being incapableof being press-fitted to both side plates 27 and 30 due to a componenttolerance can be prevented, assembly can be facilitated, and costreduction can be achieved.

The O-ring 47 is provided on the second side plate 30 side in thepresent modification example, the O-ring 47 may be provided on the firstside plate 27 side.

Modification Example 2

The pin ring mechanism 15 of the present embodiment illustrated in FIG.19 and the pin ring mechanism 15A of Modification Example 1 illustratedin FIG. 20 may be combined with each other.

Specifically, as illustrated in FIG. 18, two out of the three pin ringmechanisms are the pin ring mechanisms 15 illustrated in FIG. 19 and theremaining one pin ring mechanism is the pin ring mechanism 15Aillustrated in FIG. 20.

The present modification example has the following action and effect.

Two out of the three pin ring mechanisms have a function as apositioning pin as a configuration in which both ends of the pin 45 arepress-fitted and fixed to both side plates 27 and 30. As for the pin 45of the other pin ring mechanism, one end is press-fitted and fixed andthe other end is fixed via the O-ring 47, which results in toleranceabsorption. As a result, both side plates 27 and 30 can be positioned bymeans of the pin ring mechanism 15 and assemblability improvement can beachieved.

Eighth Embodiment

Next, an eighth embodiment of the present invention will be described.The present embodiment differs from the seventh embodiment in terms ofthe configuration of the pin ring mechanism. The eighth embodiment issimilar to the seventh embodiment regarding the other points, and thusthe points will not be described below.

As illustrated in FIG. 21, in a pin ring mechanism 15B of the presentembodiment, the first side plate 27 and the second side plate 30 areprovided with rolling bearings 49 and 51, respectively. The longitudinalcentral portion of the pin 45 is press-fitted and fixed to the centerplate 20. Both ends of the pin 45 abut against the inner peripheralsurfaces of the rolling bearings 49 and 51.

The present embodiment has the following action and effect.

The central portion of the pin 45 is press-fitted to the center plate 20and both ends of the pin 45 abut against the inner peripheral surfacesof the rolling bearings 49 and 51 provided on both side plates 27 and30. Accordingly, both ends of the pin 45 are not restrained by both sideplates 27 and 30, and thus it is possible to avoid a situation in whichthe pin 45 cannot be fixed during assembly due to the componenttolerance of both side plates 27 and 30. As a result, assemblabilityimprovement can be achieved.

O-rings (elastic bodies) 23 may be respectively provided at both ends ofthe pin 45 as illustrated in FIG. 22. Then, the impact at a time whenthe pin 45 abuts against the inner peripheral surfaces of the rollingbearings 49 and 51 can be mitigated and noise can be reduced.

Although the rolling bearings 46, 49, and 51 are adopted as membersreceiving the pin 45 in the embodiments described above, a slide bearingsuch as a floating bush bearing may be adopted instead. For example, aslide bearing 48 may be provided instead of the rolling bearing 46illustrated in FIG. 19 as illustrated in FIG. 23. Then, cost reductioncan be achieved as compared with a case where the rolling bearing isadopted. In addition, the moment of inertia of a rotation system such asthe rolling bearing can be reduced, and thus response enhancement can beachieved. Lubricant-based lubrication is required particularly in a casewhere the slide bearing is adopted, and thus more suitable is aliquid-tight structure in which the protruding wall portions 27 b and 30c of both side plates 27 and 30 are attached to each other asillustrated in FIG. 15. However, such a liquid-tight structure does notlimit the present invention including each of the embodiments describedabove.

Ninth Embodiment

Hereinafter, a ninth embodiment of the present invention will bedescribed with reference to the drawings including FIG. 24.

FIG. 24 illustrates the co-rotating scroll compressor 1. The co-rotatingscroll compressor 1 can be used as a turbocharger compressing combustionair (a fluid) supplied to an internal combustion engine such as avehicular engine, a compressor for supplying compressed air to an airelectrode of a fuel cell, or a compressor for supplying compressed airused for a braking device of a vehicle such as a railway vehicle.

The co-rotating scroll compressor 1 is provided with the housing 3, themotor (drive unit) 5 accommodated on one end side of the housing 3, andthe drive-side scroll member 70 and the driven-side scroll member 90accommodated on the other end side of the housing 3.

The housing 3 has a substantially cylindrical shape and is provided withthe motor accommodation portion 3 a accommodating the motor 5 and thescroll accommodation portion 3 b accommodating the scroll members 70 and90.

The discharge port 3 d for discharging compressed air is formed in anend portion of the scroll accommodation portion 3 b. The housing 3 isprovided with an air intake port (not illustrated in FIG. 24) suctioningair.

The motor 5 is driven by power being supplied from a power supply source(not illustrated). The rotation of the motor 5 is controlled by acommand from a control unit (not illustrated). The stator 5 a of themotor 5 is fixed to the inner peripheral side of the housing 3. Therotor 5 b of the motor 5 rotates around the drive-side rotational axisCL1. The drive shaft 6 extending on the drive-side rotational axis CL1is connected to the rotor 5 b. The drive shaft 6 is connected to thedrive shaft portion 71 d fixed to the first drive-side scroll part 71 ofthe drive-side scroll member 70.

The drive-side bearing 11 rotatably supporting the drive shaft 6 isprovided at the front end (left end in FIG. 24) of the drive shaft 6.The rear end bearing 17 rotatably supporting the drive shaft 6 betweenthe housing 3 and the rear end bearing 17 is provided at the rear end(right end in FIG. 24) of the drive shaft 6, that is, in the end portionof the drive shaft 6 that is on the side opposite to the drive-sidescroll member 70.

The drive-side scroll member 70 is provided with the first drive-sidescroll part 71 on the motor 5 side and the second drive-side scroll part72 on the discharge port 3 d side.

The first drive-side scroll part 71 is provided with the firstdrive-side end plate 71 a and the first drive-side wall body 71 b.

The first drive-side end plate 71 a extends in a direction orthogonal tothe drive-side rotational axis CL1. The drive shaft portion 71 dextending on and along the drive-side rotational axis CL1 is fixed tothe rotation center of the first drive-side end plate 71 a.

The center plate (a bearing support member) 20 is fixed to the driveshaft portion 71 d. The center plate 20 extends in parallel with thefirst drive-side end plate 71 a.

The first drive-side end plate 71 a is substantially disk-shaped in planview. As illustrated in FIG. 25, the three spiral first drive-side wallbodies 71 b, that is, the spiral first drive-side wall bodies 71 b inthe form of three flights are provided on the first drive-side end plate71 a. The first drive-side wall bodies 71 b in the form of three flightsare disposed at equal gaps around the drive-side rotational axis CL1.The first drive-side wall body 71 b may be one, two, or four or more inthe number of flights.

As illustrated in FIG. 24, the second drive-side scroll part 72 isprovided with the second drive-side end plate 72 a and the seconddrive-side wall body 72 b. The second drive-side wall body 72 b is inthe form of three flights similarly to the first drive-side wall body 71b (see FIG. 25) described above. The second drive-side wall body 72 bmay be one, two, or four or more in the number of flights.

The second drive-side shaft portion 72 c extending in the drive-siderotational axis CL1 direction is connected to the second drive-side endplate 72 a. The second drive-side shaft portion 72 c is providedrotatably with respect to the housing 3 via the second drive-sidebearing 14, which is a ball bearing. The second drive-side end plate 72a is provided with the discharge port 72 d, which is along thedrive-side rotational axis CL1.

The two seal members 26 for the second drive shaft portion are providedbetween the second drive-side shaft portion 72 c and the housing 3 andon the leading edge side (left side in FIG. 24) of the second drive-sideshaft portion 72 c beyond the second drive-side bearing 14. The two sealmembers 26 for the second drive shaft portion and the second drive-sidebearing 14 are disposed at predetermined gaps in the drive-siderotational axis CL1 direction. Enclosed between the two seal members 26for the second drive shaft portion is a lubricant that is grease such asa semi-solid lubricant. The seal member 26 for the second drive shaftportion may be one in number. In this case, the lubricant is enclosedbetween the seal member 26 for the second drive shaft portion and thesecond drive-side bearing 14.

The first drive-side scroll part 71 and the second drive-side scrollpart 72 are fixed in a state where the leading edges (free ends) of thewall bodies 71 b and 72 b face each other. The first drive-side scrollpart 71 and the second drive-side scroll part 72 are fixed by the bolt31, which is fastened to the flange portions 73 provided at a pluralityof places in the circumferential direction so as to protrude to theradial outer side.

In the driven-side scroll member 90, the driven-side end plate 90 a ispositioned substantially at the center in the axial direction(horizontal direction in the drawing). The through-hole 90 h is formedat the center of the driven-side end plate 90 a and compressed air flowsto the discharge port 72 d.

The first driven-side wall body 91 b and the second driven-side wallbody 92 b are provided on both sides of the driven-side end plate 90 a,respectively. The first driven-side wall body 91 b installed on themotor 5 side from the driven-side end plate 90 a meshes with the firstdrive-side wall body 71 b of the first drive-side scroll part 71 and thesecond driven-side wall body 92 b installed on the discharge port 3 dside from the driven-side end plate 90 a meshes with the seconddrive-side wall body 72 b of the second drive-side scroll part 72.

The three first driven-side wall bodies 91 b, that is, the firstdriven-side wall bodies 91 b in the form of three flights are providedas illustrated in FIG. 26. The driven-side wall bodies 91 b in the formof three flights are disposed at equal gaps around the driven-siderotational axis CL2. The second driven-side wall body 92 b is similar inconfiguration. Each of the driven-side wall bodies 91 b and 92 b may beone, two, or four or more in the number of flights.

The support member 33 is provided on the discharge port 3 d side (leftside in FIG. 24) of the driven-side scroll member 90. The support member33 is fixed by the bolt 25 to the leading edge (free end) of the seconddriven-side wall body 92 b.

The shank 35 a for the support member is provided on the central axisside of the support member 33 and the shank 35 a for the support memberis fixed to the housing 3 via the bearing 38 for the second supportmember, which is an angular ball bearing. As a result, the driven-sidescroll member 90 rotates around the driven-side rotational axis CL2 viathe support member 33.

The first side plate (a bearing support member) 27 is provided on themotor 5 side (right side in FIG. 24) of the driven-side scroll member90. The first side plate 27 is fixed by the bolt 28 to the leading edge(free end) of the first driven-side wall body 91 b. Formed at therotation center of the first side plate 27 is the hole portion 27 h forthe first side plate for penetration by the drive shaft portion 71 d.

The second side plate (a bearing support member) 30 is provided at apredetermined gap on the motor 5 side of the first side plate 27. Thesecond side plate 30 is fixed by the bolt 34 to the first side plate 27.Formed at the rotation center of the second side plate 30 is the holeportion 30 h for the second side plate for penetration by the driveshaft portion 71 d.

The shank 30 a for the second side plate is provided on the central axisside of the second side plate 30 and the shank 30 a for the second sideplate is fixed to the housing 3 via the bearing 32 for the second sideplate, which is an angular ball bearing. As a result, the driven-sidescroll member 90 rotates around the driven-side rotational axis CL2 viathe second side plate 30 and the first side plate 27.

The first protruding wall portion 27 b protruding toward the second sideplate 30 is provided on the outer peripheral side end surface of thefirst side plate 27. The second protruding wall portion 30 c protrudingtoward the first side plate 27 is provided on the outer peripheral sideend surface of the second side plate 30. The protruding wall portions 27b and 30 c constitute a peripheral wall portion by being attached toeach other and fixed in a liquid-tight state. As a result, the centerplate 20 disposed between the first side plate 27 and the second sideplate 30 is accommodated in the space S surrounded by both protrudingwall portions 27 b and 30 b as illustrated in FIG. 27.

As illustrated in FIG. 24, the crank pin 15 is provided between thefirst and second side plates 27 and 30 and the center plate 20. Thecrank pin 15 has the cylindrical portion 15 a at the center and thefirst eccentric shaft portion 15 b and a second eccentric shaft portion15 f, which have eccentric axes which are eccentric to the central axisof the cylindrical portion 15 a. The first eccentric shaft portion 15 bprotrudes to one side (the left side) of the cylindrical portion 15 aand the second eccentric shaft portion 15 f protrudes to the other side(right side) of the cylindrical portion 15 a. As a result, the crank pin15 has a symmetrical shape about the cylindrical portion 15 a.

Provided on the outer periphery of the cylindrical portion 15 a is thebearing 16 for the cylindrical portion (a cylindrical portion rollingbearing), which is an angular ball bearing. As a result, the cylindricalportion 15 a is rotatable with respect to the center plate 20. Alubricant such as grease is enclosed in the bearing 16 for thecylindrical portion.

The first eccentric shaft portion 15 b is provided with the bearing 34for the first eccentric shaft portion (a first crank pin end portionrolling bearing), which is an angular ball bearing. As a result, thefirst eccentric shaft portion 15 b is rotatable with respect to thefirst side plate 27. Grease (a lubricant) is enclosed in the bearing 34for the first eccentric shaft portion.

The second eccentric shaft portion 15 f is provided with a bearing 35for the second eccentric shaft portion (second crank pin end portionrolling bearing), which is an angular ball bearing. As a result, thesecond eccentric shaft portion 15 f is rotatable with respect to thesecond side plate 30. Grease (a lubricant) is enclosed in the bearing 35for the second eccentric shaft portion.

The crank pin 15 and the respective bearings 16, 34, and 35 are used assynchronization drive mechanisms transmitting a drive force from thedrive shaft portion 71 d to the driven-side scroll member 90 such thatboth scroll members 70 and 90 perform revolving and orbiting motions insynchronization.

It is preferable that a plurality of the synchronization drivemechanisms provided with the crank pin 15 are provided. For example,three synchronization drive mechanisms are provided at equal angulargaps around the rotational axes CL1 and CL2 (see FIG. 27).

FIG. 28 is an enlarged view of the part around the crank pin 15.

The bearing 16 for the cylindrical portion is provided with an outerring 16 a, an inner ring 16 b, balls 16 c disposed between the outerring 16 a and the inner ring 16 b, and a holder (not illustrated)holding the respective balls 16 c at equal gaps.

The outer ring 16 a is fitted to a circular groove formed in the centerplate 20 via an O-ring (elastic body) 36. The O-ring 36 is disposed in astate where the O-ring 36 is deformed by a predetermined amount and theO-ring 36 presses the outer ring 16 a in the inner ring 16 b direction.

The inner ring 16 b is press-fitted and fitted to the cylindricalportion 15 a.

A seal member 52 for sealing a lubricant is provided on a side (theright side in FIG. 28) of the bearing 16 for the cylindrical portion.The seal member 52 has an annular shape and the outer peripheral side ofthe seal member 52 is fixed to a side portion of the outer ring 16 a.The seal member 52 is not fixed to the inner ring 16 b and apredetermined gap is provided with respect to a side portion of theinner ring 16 b. The inner peripheral end of the seal member 52 extendsto the side portion of the inner ring 16 b. More specifically, the innerperipheral end of the seal member 52 extends to the inner peripheralside beyond the outer periphery of the inner ring 16 b.

A snap ring 55 for fixing the seal member 52 in place is provided on aside (the right side in the drawing) of the seal member 52.

The bearing 34 for the first eccentric shaft portion is provided with anouter ring 34 a, an inner ring 34 b, a plurality of balls 34 c disposedbetween the outer ring 34 a and the inner ring 34 b, and a holder (notillustrated) holding the respective balls 34 c at equal gaps.

The outer ring 34 a is fitted by press-fitting to a circular grooveformed in the first side plate 27. The inner ring 34 b is fitted to thefirst eccentric shaft portion 15 b by press-fitting.

A seal member 53 for sealing a lubricant is provided on a side (theright side in FIG. 28) of the bearing 34 for the first eccentric shaftportion. The seal member 53 has an annular shape and the outerperipheral side of the seal member 53 is fixed to a side portion of theouter ring 34 a. The seal member 53 is not fixed to the inner ring 34 band a predetermined gap is provided with respect to a side portion ofthe inner ring 34 b. The inner peripheral end of the seal member 53extends to the side portion of the inner ring 34 b. More specifically,the inner peripheral end of the seal member 53 extends to the innerperipheral side beyond the outer periphery of the inner ring 34 b.

A snap ring 56 for fixing the seal member 53 in place is provided on aside (the right side in the drawing) of the seal member 53.

The bearing 35 for the second eccentric shaft portion is provided withan outer ring 35 a, an inner ring 35 b, a plurality of balls 35 cdisposed between the outer ring 35 a and the inner ring 35 b, and aholder (not illustrated) holding the respective balls 35 c at equalgaps.

The outer ring 35 a is fitted by press-fitting to a circular grooveformed in the second side plate 30. The inner ring 35 b is fitted to thesecond eccentric shaft portion 15 f by press-fitting.

A seal member 54 for sealing a lubricant is provided on a side (the leftside in FIG. 28) of the bearing 35 for the second eccentric shaftportion. The seal member 54 has an annular shape and the outerperipheral side of the seal member 54 is fixed to a side portion of theouter ring 35 a. The seal member 54 is not fixed to the inner ring 35 band a predetermined gap is provided with respect to a side portion ofthe inner ring 35 b. The inner peripheral end of the seal member 54extends to the side portion of the inner ring 35 b. More specifically,the inner peripheral end of the seal member 54 extends to the innerperipheral side beyond the outer periphery of the inner ring 35 b.

A snap ring 57 for fixing the seal member 54 in place is provided on aside (the right side in the drawing) of the seal member 54.

The co-rotating scroll compressor 1 configured as described aboveoperates as follows.

The drive shaft 6 is rotated around the drive-side rotational axis CL1by the motor 5, and then the center plate 20 as well as the drive-sidescroll member 70 rotates around the drive-side axis CL1 via the driveshaft portion 71 d connected to the drive shaft 6. By the center plate20 rotating, the drive force transmitted to the center plate istransmitted from the first side plate 27 and the second side plate 30 tothe driven-side scroll member 90 via the crank pin 15 as asynchronization drive mechanism and the driven-side scroll member 90rotates around the driven-side rotational axis CL2. At this time, thecrank pin 15 rotates with respect to the center plate 20 and both sideplates via the respective bearings 16, 34, and 35, and thus both scrollmembers 70 and 90 relatively perform the revolving and orbiting motions.

By both scroll members 70 and 90 performing the revolving and orbitingmotions, the air suctioned from the intake port of the housing 3 issuctioned from the outer peripheral sides of both scroll members 70 and90 and taken into the compression chamber formed by both scroll members70 and 90. Then, the compression chamber formed by the first drive-sidewall body 71 b and the first driven-side wall body 91 b and thecompression chamber formed by the second drive-side wall body 72 b andthe second driven-side wall body 92 b are separately compressed. The airis compressed as the volume of each compression chamber decreases with amovement to the center side. The air compressed by the first drive-sidewall body 71 b and the first driven-side wall body 91 b passes throughthe through-hole 90 h formed in the driven-side end plate 90 a andmerges with the air compressed by the second drive-side wall body 72 band the second driven-side wall body 92 b, and the merged air isdischarged from the discharge port 3 d of the housing 3 to the outsidethrough the discharge port 72 d.

The present embodiment has the following action and effect.

As illustrated in FIG. 28, the O-ring 36 is provided between the centerplate 20 and the outer ring 16 a of the bearing 16 for the cylindricalportion. As a result, the tolerance of the crank pin 15, the side plates27 and 30, and the center plate 20 can be absorbed by the O-ring 36being deformed, internal force generation in the crank pin 15 can beavoided, and the life of the synchronization drive mechanism can beextended.

In addition, the machining tolerance of the crank pin 15 can bemitigated and machining and management costs can be reduced.

In addition, the outer ring 16 a is pressed to the inner ring 16 b sideby the O-ring 36, and thus it is possible to prevent slipping betweenthe outer ring 16 a and the hole in which the outer ring 16 a is fitted.

The outer ring 34 a of the bearing 34 for the first eccentric shaftportion and the outer ring 35 a of the bearing 35 for the secondeccentric shaft portion are press-fitted, and thus the centrifugal forcearound the rotational axes CL1 and CL2 is held by the bearings 34 and 35for the eccentric shaft portions. The two bearings 34 and 35 bear thecentrifugal force in this manner, and thus the load to be borne can bemitigated as compared with a case where the single bearing 16 for thecylindrical portion bears the centrifugal force.

In addition, the crank pin 15 is supported at both ends by the twobearings 34 and 35 for the eccentric shaft portions, and thus theposture of the crank pin 15 can be stabilized.

Modification Example 1

The present embodiment can be modified as follows. The outer ring 16 aof the bearing 16 for the cylindrical portion may be press-fitted andthe outer rings 34 a and 35 a of both bearings 34 and 35 for theeccentric shaft portions may be provided with an O-ring 37 asillustrated in FIG. 29.

Then, the tolerance of the crank pin 15, the side plates 27 and 30, andthe center plate 20 can be absorbed by the O-ring 37 being deformed,internal force generation in the crank pin 15 can be avoided, and thelife of the synchronization drive mechanism can be extended.

In addition, the machining tolerance of the crank pin 15 can bemitigated and machining and management costs can be reduced.

In addition, the outer ring 16 a is pressed to the inner ring 16 b sideby the O-ring 36, and thus it is possible to prevent slipping betweenthe outer ring 16 a and the hole in which the outer ring 16 a is fitted.

Modification Example 2

The present embodiment can be modified as follows. The outer rings 34 aand 35 a of both bearings 34 and 35 for the eccentric shaft portions maybe provided with the O-ring 37 with the outer ring 16 a of the bearing16 for the cylindrical portion provided with the O-ring 36 asillustrated in FIG. 30.

Then, the tolerance of the crank pin 15, the side plates 27 and 30, andthe center plate 20 can be absorbed by the O-rings 36 and 37 beingdeformed, internal force generation in the crank pin 15 can be avoided,and the life of the synchronization drive mechanism can be extended.

In addition, the machining tolerance of the crank pin 15 can bemitigated and machining and management costs can be reduced.

In addition, the outer ring 16 a is pressed to the inner ring 16 b sideby the O-ring 36, and thus it is possible to prevent slipping betweenthe outer ring 16 a and the hole in which the outer ring 16 a is fitted.

Modification Example 3

The present embodiment can be modified as follows.

The outer ring 16 a of the bearing 16 for the cylindrical portion andthe outer rings 34 a and 35 a of both bearings 34 and 35 for theeccentric shaft portions may be press-fitted and an O-ring 38 may beprovided between the crank pin 15 and each of the inner rings 16 b, 34b, and 35 b as illustrated in FIG. 31.

Then, the tolerance of the crank pin 15, the side plates 27 and 30, andthe center plate 20 can be absorbed by the O-ring 38 being deformed,internal force generation in the crank pin 15 can be avoided, and thelife of the synchronization drive mechanism can be extended.

In addition, the machining tolerance of the crank pin 15 can bemitigated and machining and management costs can be reduced.

The O-ring 38 may be provided only between the crank pin 15 and theinner ring 16 b of the bearing 16 for the cylindrical portion or onlybetween the crank pin 15 and the inner rings 34 b and 35 b of bothbearings 34 and 35 for the eccentric shaft portions.

Tenth Embodiment

Next, a tenth embodiment of the present invention will be described. Thepresent embodiment differs from the ninth embodiment in terms of theconfiguration of the crank pin 15. The tenth embodiment is similar tothe ninth embodiment regarding the other points, and thus the pointswill not be described below.

As illustrated in FIG. 32A, the components including the cylindricalportion 15 a and an eccentric shaft portion 15 g constitute a crank pin15′. The first eccentric shaft portion 15 b and the second eccentricshaft portion 15 f are provided at both ends of the eccentric shaftportion 15 g, respectively.

An insertion hole 15 a 1 into which the eccentric shaft portion 15 g isinserted is formed in the cylindrical portion 15 a. The eccentric shaftportion 15 g is fixed by being press-fitted into the insertion hole 15 a1.

The crank pin 15 illustrated in the ninth embodiment is illustrated inFIG. 32B. The cylindrical portion 15 a, the first eccentric shaftportion 15 b, and the second eccentric shaft portion 15 f are integratedin the crank pin 15 formed by being cut out from the same material.

The present embodiment has the following action and effect.

The eccentric shaft portion 15 g of the crank pin 15′ is inserted intothe insertion hole 15 a 1 formed in the cylindrical portion 15 a. As aresult, the eccentric shaft portion 15 g and the cylindrical portion 15a can be separate components and can be machined separately.Accordingly, the axial centers of the first eccentric shaft portion 15 band the second eccentric shaft portion 15 f at both ends of theeccentric shaft portion 15 g can be aligned as compared with a casewhere the eccentric shaft portion 15 g and the cylindrical portion 15 aare integrally machined (FIG. 32B). Accordingly, an internal forceapplied to the crank pin 15′ can be reduced and the life of thesynchronization drive mechanism can be extended.

Although the crank pin 15′ of the present embodiment can be applied inplace of the crank pin 15 of the ninth embodiment, the crank pin 15′ ofthe present embodiment is not limited to the configuration of the ninthembodiment and can be applied as a crank pin used in a co-rotatingscroll compressor.

REFERENCE SIGNS LIST

-   -   1 Co-rotating scroll compressor    -   3 Housing    -   3 a Motor accommodation portion    -   3 b Scroll accommodation portion    -   3 d Discharge port    -   5 Motor (drive unit)    -   5 a Stator    -   5 b Rotor    -   6 Drive shaft    -   11 Drive-side bearing    -   15 Crank pin (synchronization drive mechanism)    -   15 a Cylindrical portion    -   15 a 1 Insertion hole    -   15 b Eccentric shaft portion, first eccentric shaft portion    -   15 c End portion    -   15 d Small-diameter portion    -   15 e Central portion    -   15 f Second eccentric shaft portion    -   15 g Eccentric shaft portion    -   16 Bearing for cylindrical portion    -   17 Rear end bearing    -   18 a Bearing for first eccentric shaft portion (crank pin end        portion rolling bearing)    -   18 b Bearing for second eccentric shaft portion (crank pin end        portion rolling bearing)    -   19 O-ring (urging member)    -   20 Center plate    -   20 a Shank    -   20 b Fixing portion    -   21 Bolt    -   22 O-ring (elastic body)    -   23 O-ring (elastic body)    -   25 Bolt    -   26 Seal member    -   27 First side plate    -   27 a Fixing portion    -   27 b First protruding wall portion    -   27 h Hole portion for first side plate    -   28 Bolt    -   30 Second side plate    -   30 a Shank for second side plate    -   30 b Fixing portion    -   30 c Second protruding wall portion    -   30 d Drive shaft portion    -   30 h Hole portion for second side plate    -   31 Bolt    -   32 Bearing for second side plate    -   33 Support member    -   34 Bearing for first eccentric shaft portion (first crank pin        end portion rolling bearing)    -   34 a Outer ring    -   34 b Inner ring    -   34 c Ball    -   35 Bearing for second eccentric shaft portion (second crank pin        end portion rolling bearing)    -   35 a Outer ring    -   35 b Inner ring    -   35 c Ball    -   36, 37, 38 O-ring (elastic body)    -   40 Resinous shaft portion (resin portion)    -   41 Seal plate    -   42 Stopper ring    -   43 First seal member    -   44 Second seal member    -   45 Pin    -   46 Rolling bearing (ring)    -   46 a Outer ring    -   46 b Inner ring    -   46 c Ball (rolling member)    -   47 O-ring (elastic body)    -   48 Slide bearing    -   49 Rolling bearing    -   50 Drive-side scroll member    -   51 Rolling bearing    -   52, 53, 54 Seal member    -   55, 56, 57 Snap ring    -   60 Driven-side scroll member    -   61 a First driven-side end plate    -   61 d Driven shaft portion    -   70 Drive-side scroll member    -   71 First drive-side scroll part    -   71 a First drive-side end plate    -   71 b First drive-side wall body    -   71 d Drive shaft portion    -   72 Second drive-side scroll part    -   72 a Second drive-side end plate    -   72 b Second drive-side wall body    -   72 c Second drive-side shaft portion    -   72 d Discharge port    -   73 Flange portion    -   90 Driven-side scroll member    -   90 h Through-hole    -   91 First driven-side scroll part    -   91 b First driven-side wall body    -   92 b Second driven-side wall body    -   CL1 Drive-side rotational axis    -   CL2 Driven-side rotational axis    -   CL3 Eccentric axis    -   t Gap    -   S Space

1. A co-rotating scroll compressor comprising: a drive-side scrollmember driven to rotate around a rotational axis by a drive unit andhaving a spiral drive-side wall body disposed on a drive-side end plate;a driven-side scroll member in which a spiral driven-side wall bodycorresponding to the drive-side wall body is disposed on a driven-sideend plate and the driven-side wall body meshes with the drive-side wallbody to form a compression space; a synchronization drive mechanismtransmitting a drive force of the drive unit to the driven-side scrollmember such that the drive-side scroll member and the driven-side scrollmember perform rotating motions in the same direction and at the sameangular velocity; a first side plate disposed on the rotational axisdirection side with respect to the drive-side scroll member and thedriven-side scroll member; a second side plate fixed at a predeterminedgap in the rotational axis direction with respect to the first sideplate; and a center plate disposed between the first side plate and thesecond side plate, wherein the first side plate is fixed to one of thedrive-side scroll member and the driven-side scroll member, the centerplate is fixed to the other of the drive-side scroll member and thedriven-side scroll member, and the synchronization drive mechanism isprovided between the first and second side plates and the center plate.2. The co-rotating scroll compressor according to claim 1, wherein thesynchronization drive mechanism is provided with a crank pin having aneccentric shaft portion having an eccentric axis which is eccentric to acentral axis of a central cylindrical portion and a crank pin endportion rolling bearing provided between both end portions of theeccentric shaft portion and the first and second side plates, and anurging member urging an inner ring of the crank pin end portion rollingbearing toward a leading edge of the eccentric shaft portion in theeccentric axis direction is provided between the inner ring and theeccentric shaft portion.
 3. The co-rotating scroll compressor accordingto claim 1, wherein the synchronization drive mechanism is provided witha crank pin having an eccentric shaft portion having an eccentric axiswhich is eccentric to a central axis of a central cylindrical portionand a crank pin end portion rolling bearing provided between both endportions of the eccentric shaft portion and the first and second sideplates, and a preload is applied to the crank pin end portion rollingbearing in the eccentric axis direction by a gap between the first sideplate and the second side plate.
 4. The co-rotating scroll compressoraccording to claim 1, wherein the synchronization drive mechanism isprovided with a crank pin having an eccentric shaft portion having aneccentric axis which is eccentric to a central axis of a centralcylindrical portion and a crank pin end portion rolling bearing providedbetween both end portions of the eccentric shaft portion and the firstand second side plates, and an elastic body is provided between an innerperipheral surface of an inner ring of the crank pin end portion rollingbearing and an outer peripheral surface of the eccentric shaft portion.5. The co-rotating scroll compressor according to claim 1, wherein amonga fixing portion of the first side plate which is fixed to one of thedrive-side scroll member and the driven-side scroll member and a fixingportion of the center plate which is fixed to the other of thedrive-side scroll member and the driven-side scroll member, the fixingportion positioned on a radial inner side of a center of the scrollmember has a structure in which a resin portion is interposed, and thefixing portion positioned on a radial outer side of the center of thescroll member has a structure using a metal portion without resinportion interposition.
 6. The co-rotating scroll compressor according toclaim 1, wherein a peripheral wall portion surrounding an outerperipheral side of the center plate is provided between the first sideplate and the second side plate.
 7. The co-rotating scroll compressoraccording to claim 6, further comprising a drive shaft portion rotatingaround the rotational axis and connected between the drive-side endplate and the drive unit, wherein the center plate is fixed to the driveshaft portion, a hole portion for the first side plate through which thedrive shaft portion passes is formed in the first side plate, a holeportion for the second side plate through which the drive shaft portionpasses is formed in the second side plate, and a first seal member isprovided between the hole portion for the first side plate and the driveshaft portion and/or between the hole portion for the second side plateand the drive shaft portion.
 8. The co-rotating scroll compressoraccording to claim 6, further comprising a drive shaft portion rotatingaround the rotational axis and connected between the drive-side endplate and the drive unit, wherein the center plate is fixed to the driveshaft portion, a hole portion for the first side plate through which thedrive shaft portion passes is formed in the first side plate, a holeportion for the second side plate through which the drive shaft portionpasses is formed in the second side plate, and a second seal member isprovided between the first side plate and the center plate and/orbetween the second side plate and the center plate.
 9. The co-rotatingscroll compressor according to claim 6, wherein the first side plate isfixed to the drive-side wall body on an outer peripheral side, thesecond side plate is fixed to the first side plate, the drive unit isconnected to a rotation center of the second side plate, the centerplate is fixed to a driven shaft portion connected to a rotation centerof the driven-side end plate, a hole portion for the first side platethrough which the driven shaft portion passes is formed in the firstside plate, and a rotation center region of the second side plate isclosed by a wall portion.
 10. The co-rotating scroll compressoraccording to claim 1, wherein the synchronization drive mechanism isprovided with a round bar-shaped pin provided between the first andsecond side plates and the center plate and a ring guiding the pin by aninner peripheral surface of the ring abutting against an outer peripheryof the pin.
 11. The co-rotating scroll compressor according to claim 10,wherein the ring is a rolling bearing provided on the center plate, andboth ends of the pin are press-fitted to the first side plate and thesecond side plate and a longitudinal central portion of the pin abutsagainst an inner peripheral surface of the rolling bearing.
 12. Theco-rotating scroll compressor according to claim 10, wherein the ring isa rolling bearing provided on the center plate, and one end of the pinis press-fitted to one of the first side plate and the second sideplate, the other end of the pin is fixed to the other of the first sideplate and the second side plate via an elastic body, and a longitudinalcentral portion of the pin abuts against an inner peripheral surface ofthe rolling bearing.
 13. The co-rotating scroll compressor according toclaim 10, wherein three or more synchronization drive mechanisms areprovided to be spaced apart in a circumferential direction of therotational axis, in two of the synchronization drive mechanisms, thering is a rolling bearing provided on the center plate, both ends of thepin are press-fitted to the first side plate and the second side plate,and a longitudinal central portion of the pin abuts against an innerperipheral surface of the rolling bearing, and in the othersynchronization drive mechanism, the ring is a rolling bearing providedon the center plate, one end of the pin is press-fitted to one of thefirst side plate and the second side plate, the other end of the pin isfixed to the other of the first side plate and the second side plate viaan elastic body, and a longitudinal central portion of the pin abutsagainst an inner peripheral surface of the rolling bearing.
 14. Theco-rotating scroll compressor according to claim 10, wherein the ring isa rolling bearing provided on each of the first side plate and thesecond side plate, and a longitudinal central portion of the pin ispress-fitted to the center plate and both ends of the pin abut againstan inner peripheral surface of the rolling bearing.
 15. The co-rotatingscroll compressor according to claim 11, wherein the ring is a slidebearing instead of the rolling bearing.
 16. The co-rotating scrollcompressor according to claim 1, wherein the synchronization drivemechanism is provided with a crank pin having an eccentric shaft portionhaving an eccentric axis which is eccentric to a central axis of acentral cylindrical portion, a first crank pin end portion rollingbearing provided between one end of the eccentric shaft portion and thefirst side plate, a second crank pin end portion rolling bearingprovided between the other end of the eccentric shaft portion and thesecond side plate, and a cylindrical portion rolling bearing providedbetween the cylindrical portion and the center plate, and an elasticbody is provided in at least one of spaces between an outer ring of thefirst crank pin end portion rolling bearing and the first side plate,between an outer ring of the second crank pin end portion rollingbearing and the second side plate, and between an outer ring of thecylindrical portion rolling bearing and the center plate or in at leastone of spaces between an inner ring of the first crank pin end portionrolling bearing and the one end of the eccentric shaft portion, betweenan inner ring of the second crank pin end portion rolling bearing andthe other end of the eccentric shaft portion, and between an inner ringof the cylindrical portion rolling bearing and the cylindrical portion.17. The co-rotating scroll compressor according to claim 16, wherein theelastic body is provided between the outer ring of the cylindricalportion rolling bearing and the center plate, the outer ring of thefirst crank pin end portion rolling bearing is press-fitted to the firstside plate, and the outer ring of the second crank pin end portionrolling bearing is press-fitted to the second side plate.
 18. Theco-rotating scroll compressor according to claim 16, wherein aninsertion hole into which the eccentric shaft portion is inserted isformed in the cylindrical portion.
 19. The co-rotating scroll compressoraccording to claim 1, wherein the synchronization drive mechanism isprovided with a crank pin having an eccentric shaft portion having aneccentric axis which is eccentric to a central axis of a centralcylindrical portion, and an insertion hole into which the eccentricshaft portion is inserted is formed in the cylindrical portion.